TW200928155A - Stepped automatic transmission and motorcycle including the same - Google Patents

Abstract

To provide a stepped automatic transmission with four or more speeds that has simple configuration and an innovative structure. A transmission 31 includes an input shaft 52, a first rotation shaft 53, a second rotation shaft 54, and a third rotation shaft 64 that are arranged in the front-rear direction. The input shaft 52 is provided with a group of clutches 81 on the upstream side that includes a first clutch 55 and a second clutch 59. The first clutch 55 and the second clutch 59 include a first pair of shift gears 86 and a second pair of shift gears 83, respectively. The second rotation shaft 54 is provided with a group of clutches 82 on the downstream side that includes a third clutch 70 and a fourth clutch 66. The third clutch 70 and the fourth clutch 66 include a third pair of shift gears 91 and a fourth pair of shift gears 90, respectively. The group of clutches 81 on the upstream side and the group of clutches 82 on the downstream side are arranged at locations where they at least partially overlap in the axial direction of the input shaft 52.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a segment type automatic transmission and a prior art and a vehicle therefor. The motorcycle is direction-shifted by the rider leaning the body. Since motorcycles are more suitable for m-wide, in recent years, there has been an increase in demand for motorcycles that are automatically changed. Therefore, it is required to have a sleek automatic shifting device with a narrow width direction. &

❹ However, for example, in the patent document, there is disclosed a motorcycle using a three-speed segment type automatic transmission. In Patent Document i, the plurality of clutches having the segment type automatic & device are arranged in the front-rear direction. Thereby, a segment type automatic transmission having a narrow width is realized. [Patent Document 1] Japanese Laid-Open Patent Publication No. SHO 62-23349. SUMMARY OF THE INVENTION A three-speed automatic transmission according to the patent document is mounted on a crankshaft and a clutch shaft disposed on a crank reduction. There are multiple clutches. Since the crankshaft and the clutch shaft must be disposed in isolation in the front-rear direction, the power transmission between the crankshaft and the clutch shaft is performed via a key bar wound around the crankshaft and the clutch shaft.

The power of the time conveys the use of the chain's external parts. Therefore, the number of parts required for the automatic shifting and the need for a chain guide or a chain tensioner between the crankshaft and the clutch shaft is increased. Moreover, the structure of the automatic shifting device becomes complicated. Further, in the segment type automatic transmission disclosed in Patent Document 1, in order to secure the arrangement of the chain, a planetary gear is provided on the crankshaft to form a 134009.doc 200928155 to shift the crankshaft. However, planetary gears have a more complicated structure. Therefore, the structure of the automatic shifting device becomes complicated. Further, the three-speed automatic speed changing device of the third speed described in Patent Document 1 has a small number of shift speeds with respect to the speed zone of the vehicle, and therefore does not necessarily achieve a comfortable automatic shift. The present invention has been made in view of the above, and an object thereof is to provide a segmental automatic shifting device of a four-speed or higher with a novel structure having a simple structure.

❹ There is a segment type automatic transmission with a step type self-shaft of the present invention. The segmented automatic transmission of the present invention comprises: [rotating shaft, slave shaft, third rotating shaft connected to the output shaft or forming the output shaft, wheel pair, flute idle gear pair, second clutch, second Gear shifting machine: transmission gear pair, second transmission gear pair, first-one-way rotation delivery mechanism or second single & speed gear pair, snapper rotation transmission mechanism, third clutch, third variable fourth clutch And a fourth shifting gear pair. Arrangement of the rotating shaft system The rotating shaft system is arranged in a direction perpendicular to the axial direction of the input shaft. The second series are arranged in the direction perpendicular to the axial direction of the two. The third axis of rotation is formed in the output sleeve i: the direction perpendicular to the axis. The third rotating shaft system connection w 4 constitutes the wheeling shaft. The first clutch and the piece. The first off-body] is configured to enter the side clutch member and the output side clutch. The input side clutch members of the first to the eleventh are rotated together with the input shaft. The output side clutch member of σ 15 can be rotated for the input shaft 134009.doc, and the first clutch and the first clutch have the first gear and the second gear. ί # wheel bite, the second gear is transmitted with: _. The second gear train has a second clutch having a twisting mechanism and a first rotating shaft. Pieces. The first-private, input side clutch member is a clutch output side clutch. The first-private input side clutch member is multiplied by a. The output of the clutch is balanced with the input shaft. The second ejector member is capable of crying the clutch system and the enthalpy to the input shaft. The second clutch piano is connected to the upstream clutch. , the rotational speed of the input shaft of the first clutch is the second variable gear pair and the first clutch and the second clutch have the third gear and the fourth gear. The third gear train rotates together with the third gear bite 1 out side clutch member. The fourth gear train has two shifting gears, and the fourth gear train rotates with the first rotating shaft. The first pass has a different gear ratio than the first shifting gear pair. The hand wheel pair has a fifth tooth tone # with the first axis of rotation _ , face 褙 and the first, the gear. The fifth gear train ❹ six gear trains with the :::::. The sixth gear train meshes with the fifth gear. The first brother rotates together with the axis of rotation. The transmission gear pair has a seventh gear and an eighth gear. The seventh gear train rotates together with a rotating shaft. The eighth gear train meshes with the seventh gear. The eighth gear train rotates together with the third rotating shaft. The first one-way rotating transmission mechanism is disposed on the second rotating shaft and the first rotating shaft. The first one-way rotation transmission mechanism transmits the rotation of the second rotation shaft to the seventh gear. The first-one-way rotation transmission mechanism does not transmit the rotation of the seventh gear to the second rotation shaft. The rotation transmitting mechanism is disposed between the third rotating shaft and the eighth gear 134009.doc -11 ^ 200928155. The first dry rotation transmitting mechanism is the eighth sound % three rotating shaft. The first gear is transmitted to the first gear The early rotation transmitting mechanism is transmitted to the eighth gear. The third clutch of the second rotating shaft of the liver has an input side clutch. The third side of the tester and the input side clutch of the output side clutch The member rotates. The third person is crying at the private mountain / the first rotating shaft together with the output side of the alpha clutch shaft is rotated ❶ the member can be the second rotating and the third variable gear pair has the output side of the ninth gear and the third clutch The ninth gear train of the clutch member is engaged with the ninth gear. The tenth gear rotates the tenth gear train-趟, the spear-burning shaft together with the spinner. The second shift gear pair has the same gear shifting gear as the J. And the second change of the different gear ratios. The fourth clutch of the 遑 gear pair has an input side away from the #. The fourth Μ人#± thief member and the output side clutch member of the fourth clutch input side clutch spine. The fourth Hertz is fast, and the output side clutch member of the yoke is rotatable with respect to the shaft. The fourth clutch system and the first and the second group are combined with the fourth clutch and the first: The clutch rotation speed is connected. The fourth shift gear pair of the second rotation shaft is the same as the eleventh gear train and the fourth clutch gear.... and the twelfth gear wheel. Tenth - the output side of the device Clutch member one + 〇 turn tenth... Twelve gear train and third rotating shaft - same grain rotation. Fourth shift gear silver, * ice · 4^4 * αβ 变 迷 齿轮 gear pair, second shift gear pair and The third shifting wire has the same meaning as the present invention. The self-propelled shifting device, the upstream clutch group 134009.doc • 12- 200928155 and the downstream clutch group are disposed at least in the axial direction of the input shaft. ° (Effect of the invention) According to the present invention, Realization - Recording and ancient ts SS #, Mussels now have a novel structure with a simple structure and a four-speed or more segmented automatic transmission. [Embodiment] . "Implementation 1" In this embodiment 1, An example of a suitable embodiment of the present invention will be described as an example of a motorcycle of the present invention, which is a pedal type vehicle shown in Fig. 1. In the present invention, the "motorcycle" is not limited to a scooter type vehicle. . "Motorcycle" means the so-called generalized motorcycle. Specifically, in the present specification, "motorcycle" means all vehicles that are direction-shifted by tilting the vehicle. Therefore, "Mr. Red - - ΤΓ KB ! U Ο - thick car" is not limited to locomotives. At least one of the front wheel and the rear wheel may be constituted by a plurality of wheels. Specifically, the "motorcycle" is a vehicle in which at least one of the front wheel and the rear wheel is constituted by two vehicle wheels arranged adjacent to each other. "Motorcycles" include at least motorcycles in the narrow sense, pedal-type vehicles, light-duty treadmills and off-road vehicles. - (Schematic Structure of Pedal-Type Vehicle 1) First, a schematic configuration of a pedal-type vehicle will be described with reference to Fig. 1 . Further, in the following description, the directions of the front, rear, left, and right directions refer to the direction of the rider riding on the seat cushion 1 of the scooter type vehicle 1. The scooter type vehicle 1 includes a body frame 10 . The body frame 1A has a head (not shown) attached to the front portion of the vehicle, and is slightly inclined downward toward the front. A steering link (not shown) is rotatably inserted into the head pipe. The upper end is provided with a handle 12 at 134009.doc -13- 200928155. On the other hand, the steering link is connected to the lower end of the front fork 15, and the (four) 16 as the driven wheel is dry. A body cover 13 is attached to the body frame 10 at a turn. The body frame 1〇 is covered by the body cover u. The body cover 13 has a foot guard 27: a wrong guard plate 27m ± (four) anti-wei 27. With the chat

Shame the front of the vehicle. Further, the body cover 13 has a foot implant A' which is disposed rearward of the foot guard plate 27 and is disposed in the vehicle:

A foot mounting surface 17a is formed on the foot mounting table 17. The pedal type handle ^ the passenger's foot is placed on the foot mounting surface 17a. Vertical = between the left and right foot mounting tables 17, and a central cover 26 constituting one of the body cover 13 is disposed. The center cover 26 protrudes upward from the foot mounting surface 17& of the foot mounting table 17, and forms a tunnel shape extending in the front-rear direction. A seat 骑14 for the rider is mounted on a portion of the body cover u that is rearward of the center cover 26. Further, the side frame 23 is mounted on the body frame of the vehicle.

As soon as the body frame 10 is slidably suspended, the engine unit 2 is suspended. Specifically, the engine unit 20 is a rocking unit type engine. An engine bracket 21 is integrally coupled to the engine unit 2''. The engine unit 2 is pivoted by the engine bracket 21 to the pivot of the body frame 10. Further, the end of the pad unit 22 is mounted on the engine unit 2A. The other end of the engine unit 2 () is attached to the rear of the body frame 10. The tilting of the engine unit 2 is suppressed by the pad unit 22. The engine unit 20 is provided with an output shaft 33 (refer to Fig. 2) that outputs power generated by the engine unit 20. The rear wheel 18 is mounted to the output shaft 33. Therefore, the rear wheel 18 is 134009.doc -14- 200928155 driven by the power generated by the engine unit 20. In summary, in the present embodiment 1, the rear wheel 18 constitutes a drive wheel. As shown in Fig. 2, in the present embodiment, a vehicle speed sensor 88 is provided for the output shaft 33. Specifically, the vehicle speed sensor 88 is provided for the fourteenth gear 80 that rotates together with the output shaft η. However, the vehicle speed sensor 88 can also be provided for a rotating shaft other than the output shaft 33. (Structure of Engine Unit 20) ❺ FIG. 2 is a cross-sectional view of the engine unit 2〇. Fig. 4 is a schematic view showing the structure of the engine unit 2''. As shown in Fig. 2, the engine unit 20 is provided with an engine 3A and a shifting device 31. Further, this embodiment i illustrates an example in which the engine 3 is a single-cylinder engine. However, in the present invention, the engine 30 is not limited to a single cylinder engine. The engine 3 can also be a multi-cylinder engine such as a 2-cylinder engine. - Engine 30 - The engine 30 includes a crankcase 32, a cylinder block 37, a cylinder head 40, and a crankshaft 34. Inside the crankcase 32, a crank chamber 35 is defined. Inside the cylinder 37, ❹ σ 卩 ' is divided into cylinders 38 which are opened in the crank chamber 35. A cylinder head 40 is attached to the front end of the cylinder block 37. The crank chamber 35 is provided with a crank shaft 34 extending in the vehicle width direction. A link 36 is attached to the crankshaft 34. At the front end of the link 36, a piston 39 disposed in the cylinder 38 is mounted. The combustion chamber 41 is divided by the piston 39, the cylinder block 37, and the cylinder head 40. At the cylinder head 4, the ignition plug 42 is attached so that the ignition portion of the front end is located in the combustion chamber 41. 3 is a partial cross-sectional view showing the engine unit 20 of the kick starter 1 and the battery cell 1〇i. As shown in Figs. 1 and 3, a foot starter 1 is provided in the engine unit 20. The pedal type vehicle rider can operate the kick starter 100 by 134009.doc 200928155 to start the engine 30. The kick starter 100 has a foot pedal 24. As shown in FIG. 1, the footrest 24 is disposed on the left side of the crankcase 32 behind and above the crankshaft 34. As shown in Fig. 3, the foot board 24 is attached to the pedal shaft 1〇2. A compression coil spring 丨〇3 is provided between the pedal shaft 1〇2 and the crankcase 32. The compression coil magazine i 〇 3 is applied to the pedal 丨〇 2 which is rotated by the rider's operation, and is biased in the reverse rotation direction. Further, a gear 1〇4 is provided on the pedal shaft 1〇2. On the other hand, a gear 1〇6 is provided on the shaft 105 so as not to be rotatable. The gear ι 4 is engaged with the gear 106. With the gear 104 and the gear 1〇6, the rotation of the pedal shaft 1〇2 is transmitted to the shaft 105. A ratchet 1〇7 is formed on the shaft 105. A portion of the shaft 1〇5 is formed with a ratchet 1〇7, and a ratchet 108 is mounted. If the shaft 105 rotates, the ratchet 1〇8 is guided by the ratchet 1〇7 and moved to the axial right side of the shaft 105. On the other hand, if the shaft 〇5 is reversely rotated by the urging force of the compression coil spring 103, the ratchet 1〇8 is guided by the ratchet 107 and moved to the left side in the axial direction of the shaft 1〇5. A fastening portion 109 is formed on the right end surface of the ratchet 108. On the other hand, a snap portion 110 is formed on the left end surface of the gear 111 rotatably provided on the shaft 105. The engaging portion 109 of the ratchet 108 is engaged with the engaging portion 110 when the ratchet 108 moves to the right. Thereby, when the ratchet 1〇8 moves to the right, the rotation of the shaft 105 is transmitted to the gear 111. The gear ill is engaged with the gear 116 formed on the balancer shaft 115. Further, the gear 116 is engaged with the gear 117 formed on the crank pump 34. Thereby, the rotation of the gear ill is transmitted to the crankshaft 34 via the balancer shaft 115. Therefore, when the foot board 24 is operated, the crank pump 34 is rotated and the engine 30 is started. Further, the pedal shaft 102 extends from the center side of the vehicle so as to straddle the transmission 31 in a plan view. That is, as shown in Fig. 3, the pedal shaft 1〇2 is disposed so as to extend from the left side in the vehicle width direction toward the center of the vehicle body, and is arranged in one portion of the shifting device 31 and in the vertical direction. Further, the engine 30 is also provided with a battery cell motor 101. The battery cell motor 101 is mounted to the crankcase 32. The rotation of the battery cell 101 is transmitted to the crankshaft 34 via the gears 120, 121 and 122. Thereby, the battery cell motor 101 is driven by the operation of the rider, whereby the engine 30 is started. ^ - Generator 45 - A generator cover 43 is mounted on the right side of the crankcase 32. A generator chamber 44 is defined by the generator cover 43 and the crankcase 32. The right end of the crankshaft 34 projects from the crank chamber 35 and reaches the generator chamber 44. A generator 45 is attached to the right end of the crankshaft 34 in the generator chamber 44. The generator 45 includes an inner member 45a and an outer member 45b. The inner member 45a is rotatably mounted to the crankcase 32. On the other hand, the outer member 4讣 Φ is attached to the right end of the crankshaft 34. The outer member 45b rotates in the same manner as the crank shaft 34_. Therefore, if the crank shaft 34 rotates, the outer member 45b will relatively rotate with respect to the inner member 45a. Thereby generating electricity. Further, a fan 46 is provided to the outer member 4''. Cooling of the bow engine 30 is performed by the fan 46 rotating together with the crankshaft 34. A shifting device cover 5 is attached to the left side of the crankcase 32. The shifting device cover 50 and the crankcase 32 are divided to form a shifting device chamber on the left side of the crankcase 32 - the structure of the shifting device 31 - 134009.doc -17 - 200928155 Next, the shifting will be described in detail with reference mainly to FIG. The structure of the device 31. The transmission 31 is provided with a four-speed automatic transmission of the input shaft 52 and the output shaft 33. The shifting device 31 is a so-called gear train type automatic shifting device that transmits power from the input shaft 52 to the output shaft 33 via a plurality of shifting gear pairs. As shown in Fig. 2, the left end portion of the crank shaft 34 protrudes from the crank chamber 35 and reaches the shifting device chamber 51. The crankshaft 34 also serves as an input shaft of the shifting device 31. 52 ° © - Rotary shaft structure - The shifting device 31 has a first rotating shaft 53, a second rotating shaft 54, a third rotating shaft 64, and an output shaft 33. The first rotating shaft 53, the second rotating shaft 54, the third rotating shaft 64, and the output shaft 33 are arranged in parallel with the input shaft 52, respectively. In Fig. 5, the symbols C1, C2, C3, C4, and C5 represent the axis of the input shaft 52, the axis of the first rotary shaft 53, the axis of the second rotary shaft 54, the axis of the third rotary shaft 64, and the output shaft 33, respectively. The axis. As shown in FIG. 5, the input shaft 52, the first rotating shaft 53, the second rotating shaft 54, the third rotating shaft 64, and the output shaft 33 are arranged sideways to be perpendicular to the axial direction of the input shaft 52. About - slightly horizontal. More specifically, the axis C1 of the input shaft 52, the axis C2 of the first rotating shaft 53, the axis C3 of the second rotating shaft 54, the axis C4 of the third rotating shaft 64, and the axis C5 of the output shaft 33 are seen from the side , arranged on a straight line about the approximate level. Thus, by arranging the respective rotation axes, the distance between the input shaft 52 and the output shaft 33 can be relatively increased. Further, in Fig. 5, the symbol % indicates an idle gear. Symbol 95 denotes a one-way gear for a starter. Further, in the present embodiment, an example will be described in which the output 134009.doc -18. 200928155 axis 33 and the third rotation axis 64 are individually set. However, the present invention is not limited to this structure. The wheel shaft 33 and the second rotating shaft 64 may be common. In other words, it is also possible to mount the rear wheel is for the third rotating shaft 64. The upstream side clutch group 81 is provided with the upstream side clutch group 81 on the input shaft 52. The upstream clutch group 81 includes a weir clutch 55 and a second clutch 59. The first clutch 55 is disposed on the right side of the second clutch 59. The first clutch 55 and the second clutch 59 are each constituted by a centrifugal clutch. Specifically, in the first embodiment, the first clutch 55 and the second clutch 59 are each constituted by a drum type centrifugal clutch. However, the present invention is not limited to this structure. The first clutch and the second clutch 59 may be clutches other than the centrifugal clutch. For example, the first clutch 55 and the second clutch 59 may be hydraulic clutches. Among them, the first clutch 55 is preferably a centrifugal clutch. The first clutch 55 includes an inner member "as an input side clutch member" and an output side clutch (four) outer member 57. The inner member 56 is rotatably provided to the input cymbal 52. Therefore, the inner member 56 is coupled to the input shaft 52. Rotation-co-rotation. Another aspect 'outer member 57 can be rotated for input pumping 52. • If the rotational speed of input shaft 52 is greater than a particular rotational speed, inner member 56 and outer member 57 due to centrifugal force acting on inner member 56. In this case, the first clutch 55 is turned on. On the other hand, when the inner member % and the outer member are rotated, if the rotational speed is less than the specific rotational speed, the inner member 56 is applied. The centrifugal force is weakened, and the inner member % is separated from the outer member edge. Thereby, the first clutch 55 is opened. The second clutch 59 is provided with an inner member as an output side clutch member and 134009.doc -19- 200928155 inner member 60 For the latter

The centrifugal force of the inner member 60 is weakened, and the inner member 6 is "separated from the outer member. Thereby, the second clutch 59 is disconnected. As the input side clutch member outer member 61. The third gear 62 of the inner member cannot be rotated. When the input shaft 52 rotates via the first shift gear pair 86, the first rotating shaft 53, and the second, in the present embodiment 1, the outer member 57 and the outer member 61 are configured by the same member. The outer member blade and the outer member 61 may be configured by different members. The rotational speed of the input shaft 52 when the first clutch 55 is connected and the rotational speed of the input shaft 52 when the second clutch 59 is connected In other words, when the first clutch 55 is connected, the rotational speed of the inner member 56 is different from the rotational speed of the inner member 6〇 when the first clutch 59 is connected. Specifically, e, when the first clutch 55 is connected The rotational speed of the input shaft 52 is lower than the rotational speed of the input shaft 52 when the second clutch 59 is connected. More specifically, the rotational speed of the first clutch 55 to the input shaft 52 is equal to or higher than the first rotational speed. On the other hand, the first clutch 55 is in an open state when the rotational speed of the input shaft 52 is smaller than the first rotational speed. The rotational speed of the second clutch 59 based on the input shaft 52 is higher than the first one. When the second rotation speed is equal to or higher than the second rotation speed, the second clutch 59 is in a state of being broken when the rotation speed of the input shaft 52 is smaller than the second rotation speed. The first clutch 55 is an outer member 57, and the first gear 58 is non-rotatably disposed to the outer member 57. The first gear 58 rotates together with the outer member 57 of the first clutch 55. On the other hand, the first rotating shaft 53 is provided with a second tooth-wheel 63. The second gear 63 is engaged with the first gear 58. The first gear 58 and the second gear 63 are combined with the first shift gear pair 86. In this embodiment, the The shift gear pair 86 constitutes a first speed shift gear pair. The second gear 63 is a so-called one-way gear. Specifically, the second gear train transmits the rotation of the first gear 58 to the first rotary shaft 53. Aspect, the second gear 63 will not be the first The rotation of the rotating shaft 53 is transmitted to the input shaft 52. The second gear 63 is provided with a one-way rotation transmitting mechanism 96. The inner member 6A as the output side clutch member of the second clutch 59 is provided with the second gear 62. The third gear 62 rotates together with the inner member 6〇. ❹ In another aspect, the fourth gear 65 is disposed on the first rotating shaft 53. The fourth gear 65 is engaged with the third gear 62. The fourth gear 65 and The third gear train is constituted by the first shift gear pair 83. The second shift gear pair 83 has a gear ratio different from that of the first shifting gear * 86. Specifically, the third shift gear pair 83 has a smaller than the first shifting gear Gear ratio of gear pair 86. The second shifting gear pair 83 constitutes a second speed shifting gear pair. The first clutch 55 and the second clutch 59 are located between the first shift gear pair 86 and the second shift gear pair 83. In other words, the first clutch 55 and the second clutch 59 are disposed between the first shift gear (four) and the second variable gear pair 134009.doc - 21 · 200928155 83. The "state" fourth gear 65 also functions as the fifth gear π. In other words, the fourth gear 65 and the fifth gear 87 are common. The sixth gear 75 is disposed on the second rotation shaft 54' for the second rotation. The sixth gear 75 is rotated in the same manner as the mth "unrotable first-rotating shaft. The fifth gear 87 having the function of the second fourth gear 65 is also engaged with the k-gear 75. It is also provided as the fourth gear 65-wheel 75. The fifth gear 87 and the sixth tooth constituting the first transmission gear pair 84 are on the second rotation shaft 54, and the 笫4* is also rotated by the human body. The seventh gear 74 is not ancient for the second rotation shaft 54. The gear 74 rotates in the same manner as the second rotating shaft 54. In addition, in the third rotating shaft 64, the eighth gear 78 is non-rotatably provided for the first rotating sleeve 64. The third rotation is performed. The fourth gear 78 is coupled to the sneaker wheel 86. The seventh gear 74 and the train wheel constitute a second transmission gear pair 85. The eighth gear 78 is a so-called one-way gear. The rotation of 54 is transmitted to the third rotation: the eighth _ series eighth gear 78* will be the third rotation (four) 4 ° the other side ' 54. In summary, the first person ϋ to the second axis of rotation but in the present invention The eighth gear 7 is provided with a one-way rotation transmission mechanism 93. For example, the eighth gear 78 is a so-called one-way gear. The seventh gear 74 of the whistle may be a so-called one-way gear. Specifically, the seventh=the unidirectional rotation transmitting mechanism is also provided to the eighth gear 78, and the other is not the rotation of the second rotating shaft 54. The second rotation shaft 54 may be transmitted. The rotation of the eighth gear 不 is not transmitted to 134009.doc • 22- 200928155 ～ the downstream side clutch group 82 〜 the second rotation shaft 54 is provided with the downstream side clutch group 82. The downstream side clutch group 82 is located behind the upstream side clutch group 81. As shown in Fig. 2, the downstream side clutch group 82 and the upstream side clutch group 81 are disposed at least a part of the position of the input shaft 52 in the axial direction. In other words, downstream The side clutch group 82 and the upstream side clutch group 81 are disposed at least partially overlapping each other in the vehicle width direction. Specifically, the downstream side clutch group 82 and the upstream side clutch group 81 are disposed in the vehicle width direction. The downstream clutch group 82 includes the third clutch 70 and the fourth clutch 66. The fourth clutch 66 is disposed on the right side of the third clutch 70. Therefore, the first clutch 5 is provided. 5, the direction in which the second clutch 59 is located is equal to the direction in which the fourth clutch 66 is located for the third clutch 70. Then, as shown in FIG. 2, the first clutch 55 and the fourth clutch 66 are configured to be At least a portion of the vehicle width direction overlaps. In other words, the first clutch 55 and the fourth clutch 66 are disposed to overlap at least a portion with respect to the axial direction of the input shaft 52. On the other hand, the second clutch 59 and the third clutch The 〇 is configured such that at least a portion overlaps with respect to the vehicle width direction. In other words, the second clutch 59 and the second clutch 7 are configured to overlap at least a portion with respect to the axial direction of the input shaft 52. Specifically, the first clutch 55 and the fourth clutch are disposed so as to substantially overlap with respect to the vehicle width direction. On the other hand, the second clutch 59 and the third clutch 7 are disposed so as to substantially overlap with respect to the vehicle width direction. ° ' The third clutch 70 and the fourth clutch 66 are respectively formed by a hydraulic clutch structure 134009.doc • 23· 200928155. Specifically, in the first embodiment, the third clutch 70 and the fourth clutch 66 are each constituted by a disc type hydraulic clutch. However, the invention is not limited to this structure. The fourth clutch 66 and the third clutch 70 may also be clutches other than the hydraulic clutch. For example, the fourth clutch 66 and the third clutch 7〇 may also be centrifugal clutches. However, the fourth clutch 66 and the third clutch 7 are suitable for the hydraulic clutch. - In this manner, the first clutch 55, the second clutch 59, the fourth clutch 66, and the second clutch 70 may each be a drum type or a disc type centrifugal clutch, or a drum type or a disc type hydraulic clutch. The first clutch 55, the second clutch 59, the fourth clutch 66, and the third clutch 70 are all centrifugal clutches, and the first clutch 55, the second clutch 59, the fourth clutch 66, and the third clutch 70 are all hydraulic clutches. can. Further, the first clutch first clutch 59, the fourth clutch 66, and the third clutch 7 〇 may have a larger gear or a plurality of clutches other than the centrifugal clutch #. The smaller clutch may be a hydraulic clutch. Specifically, only the first yoke 55 is a centrifugal clutch, and the other clutches 59, 66, and 70 are hydraulically driven. Conversely, the gears of the first clutch 55, the second clutch 59, the fourth clutch "and the third clutch 7" are relatively large! One or a few clutches are hydraulic clutches, and the gears other than the smaller ones are smaller. For the centrifugal clutch, the rotational speed of the second rotating shaft 54 when the first clutch 7Q is connected and the rotational speed of the second rotating shaft 54 to which the fourth clutch is connected are different from each other. The rotational speed of the inner member 71 when the clutch 70 is engaged with the rotational speed of the inner member 67 when the fourth clutch 66 is connected is not the same as the rotational speed of the rotary shaft 54 of the second rotary shaft 54 4 ❹ 200928155. The third rotation speed when the third clutch 70 is connected is lower than the second rotation speed when the fourth clutch 66 is connected. The third clutch 70 includes the inner member η as the input side clutch member and the output side clutch member. The outer member 72. The inner member 71 is non-rotatably provided for the second rotating shaft 54. Therefore, the inner member 71 rotates with the rotation of the second rotating shaft 54. On the other hand, the outer member 72 can be The second rotating shaft 54 rotates. When the third rotating shaft 54 is not turned on, if the second rotating shaft 54 rotates, the inner member 71 rotates together with the second rotating shaft 54, and the outer member 72 does not. Rotating together with the second rotating shaft 54. When the third clutch 70 is turned on, both the inner member 71 and the outer member 72 rotate together with the first rotating shaft 54. The output side clutch member as the third clutch 70 The outer member 72 is provided with a ninth gear 73. The ninth gear 73 rotates together with the outer member 72. On the other hand, on the third rotating shaft 64, the tenth gear 77 is not rotatable to the third rotating shaft 64. The tenth gear 77 is rotated together with the third rotating shaft. The ninth gear 73 and the tenth gear 77 are engaged with each other. Therefore, the rotation of the outer member 72 is transmitted to the third rotating shaft 64 via the ninth gear 73 and the tenth gear 77. The ninth gear 73 and the tenth gear 77 constitute a third shift gear pair 91. The gear ratio of the third shifting gear pair 91 to the first shifting gear pair 86, the gear ratio of the second shifting gear pair 83, and the gear ratio of the fourth shifting gear pair 9〇 have different gear ratios. The third shifting gear pair 91 is for the third clutch 7 〇 and is located on the same side of the second shifting position I34009.doc • 25- 200928155 # wheel pair 83 for the second clutch 59. Specifically, the third shift gear pair 91 is located on the left side with respect to the third clutch 7''. Similarly, the second shifting gear pair 83 is located on the left side with respect to the second clutch 59. Further, the third shift gear pair 91 and the second shift gear pair (2) are arranged such that at least a part of them overlap each other with respect to the vehicle width direction. In other words, the third idle gear pair 91 and the second shift gear pair 83 are disposed such that at least a portion overlaps each other with respect to the axial direction of the input shaft 52. Specifically, the third shift gear pair 91 and the second shift gear pair 83 are disposed so as to substantially overlap with respect to the vehicle width direction. The fourth clutch 66 includes an inner member as an input side clutch member and 7 is an output side clutch member outer member 68. The inner member 67 is provided so as to be non-rotatable to the second rotating shaft 54. Therefore, the inner member 67 is tied to the second member The rotation of the rotating shaft 54 rotates together. On the other hand, the outer member "can rotate for the second rotating shaft 54. In a state where the fourth clutch 66 is not turned on, if the second rotating shaft 54 rotates, the inner member 67 is rotated together with the second rotating shaft, and the outer member 68 does not overlap with the second rotating shaft 54. In the state in which the fourth clutch 66 is turned on, the inner member 67 and the outer member "both sides rotate with the second rotating shaft 54. The eleventh gear 69 is attached to the output side clutch member outer member 68 as the fourth clutch 66. The eleventh gear 69 rotates together with the outer member 68. On the other hand, on the third rotating shaft 64, the twelfth gear 76 is rotatably provided to the third rotating shaft 64. The twelfth gear 76 rotates in the same manner as the third rotary shaft 64. The eleventh gear 69 and the twelfth gear are redundantly engaged with each other. Therefore, the rotation of the outer member 68 is transmitted to the third rotating shaft 64 via the eleventh gear 69 and the twelfth tooth 134009.doc -26- 200928155 wheel 76. The twelfth gear 76 and the eleventh gear 69 constitute a fourth shift gear pair 卯. The gear ratio of the fourth shifting gear pair 9 to the first shifting gear pair % and the gear ratio of the first shifting gear pair 83 have different gear ratios. The third clutch 7A and the fourth clutch 66 are located between the third shift gear pair ... and the fourth shift gear pair 9A. In other words, the third clutch 7A and the fourth clutch 66 are disposed between the third shift gear pair 91 and the fourth shift gear pair 90. The fourth shifting gear pair 90 is for the fourth clutch 66, and is located at the side of the first shifting gear pair 86 with respect to the first clutch 55. Specifically, the fourth shifting gear pair 9 is for the fourth clutch 66. Located on the right side. The first shifting gear pair 86 is also located to the right side with respect to the first clutch 55. Further, the fourth shift gear pair 90 and the first shift gear pair 86 are disposed such that at least a part of them overlap each other with respect to the vehicle width direction. In other words, the fourth shifting gear pair 90 and the first shifting gear pair 86 are arranged to overlap each other with respect to the axial direction of the input shaft ^ and at least a portion. Specifically, the fourth shift gear pair 90 and the first shift gear pair 86 are arranged to substantially overlap with respect to the vehicle width direction. On the third rotating shaft 64, the thirteenth gear 79 is "unrotatably provided for the third rotating shaft. The thirteenth gear 79 is disposed in the vehicle width direction, compared to the twelfth gear 79 and the tenth gear 77. On the left side, the thirteenth gear 79 is rotated in the same manner as the third rotating shaft 64. The other side is placed on the output shaft 33, and the fourteenth gear 80 is rotatably provided to the output shaft 33. In other words, The fourteenth gear 80 rotates together with the output shaft 33. The fourth transmission gear 98 is constituted by the fourteenth gear 8〇 and the 134009.doc -27-200928155 thirteenth gear 79. By the third transmission gear 98. The rotation of the third rotating shaft 64 is transmitted to the output shaft 33. ~ Detailed configuration of the downstream side clutch group 82 - Next, the downstream side clutch group 82 will be described in detail with reference mainly to Figs. 6 to 8

A plate group 136 is provided to the third clutch 70. The plate group 136 includes a plurality of friction plates 134 and a plurality of clutch plates 135. The plurality of friction plates 134 and the plurality of clutch plates 135 are laminated in the vehicle width direction in a mutually different manner. The friction plate 134 is not rotatable to the outer member 72. On the other hand, the clutch plate 135 is not rotatable to the inner member 71. The inner member 71 is rotatable to the outer member 72. "The stress plate 163 is disposed on the opposite side of the inner member 71 from the outer member 72 in the vehicle width direction. The stress plate 163 is biased to the right side in the vehicle width direction by the compression coil spring 92. That is, the stress plate 163 is biased toward the hub portion ι62 side by the compression coil spring 92. An operation chamber 137 is defined between the hub portion 162 and the stress plate 163. The operation chamber 137 is filled with oil. When the hydraulic pressure in the operation chamber 137 becomes high, the stress plate 163 is displaced in a direction away from the hub portion 162. Thereby, the distance between the stress plate 163 and the inner member 71 becomes short, and the plate group 136 is pressed against each other. As a result, the inner member 71 and the outer member 72 rotate together, and the third clutch 70 is in a connected state. On the other hand, if the pressure in the operation chamber 137 is low, the stress chamber 163 is displaced toward the wheel portion 162 side by the compression coil spring 92. Thereby, the crimping state of the plate group 136 is released. As a result, the inner member 71 and the outer member 72 can be rotated together to open the third clutch 7''. 134009.doc -28- 200928155 - Further, although not shown, a leakage hole that communicates with the operation to 137 is formed in the third clutch 7?. Moreover, the inner member 71 and the outer member are not sealed. Thereby, the oil in the operation chamber 137 can be quickly discharged when the clutch 70 is turned off. Therefore, according to this embodiment, the reactivity of the clutch can be improved. Further, according to the present embodiment, the other sliding portion can be smoothly lubricated by the oil scattered from the leak hole or the gap between the inner member 71 and the outer member 72. A plate group 132 is provided to the fourth clutch 66. The plate group 132 is provided with a plurality of friction plates and a plurality of clutch plates 131. The plurality of friction plates 130 and the plurality of clutch plates 131 are laminated in the vehicle width direction in a mutually different manner. The friction plate 13 is not rotatable to the outer member 68. On the other hand, the clutch plate m is not rotatable to the inner member 67. The inner member 67 is rotatable to the outer member 68 and displaced in the vehicle width direction. The stress member 161 is placed on the side of the inner member 67 opposite to the outer member 68 in the vehicle width direction. The stress plate 161 is biased to the left side in the vehicle width direction by the compression coil spring 89. That is, the stress plate 161 is biased toward the hub portion 162 by the compression coil spring 89. An operation chamber 133 is defined between the hub portion 162 and the stress plate 161. The operating room 133 is filled with oil. When the hydraulic pressure in the operation chamber 133 becomes high, the stress plate 161 is displaced in a direction away from the hub portion 162. Thereby, the distance between the stress plate 161 and the inner member 67 becomes short. Therefore, the plate group 132 is pressed against each other. As a result, the inner member 67 and the outer member 68 rotate together, and the fourth clutch 66 is in a connected state. On the other hand, if the pressure in the operation chamber 133 becomes low, the stress chamber 161 is 134009.doc -29- 200928155 and is displaced toward the hub portion 162 side by the compression coil spring 89. Thereby, the crimping state of the plate group 132 is released. As a result, the inner member 67 and the outer member (10) can be rotated relative to each other to open the fourth clutch 66. Further, although not shown, the fourth clutch 66 is formed with a small leak that communicates with the operation chamber 133; Moreover, the inner member 67 and the outer member are not sealed. Thereby, when the clutch 66 is opened, the oil in the operating chamber 133 can be quickly discharged. Therefore, according to this embodiment, the clutch 66 < reactivity can be improved. Further, according to the present embodiment, the other sliding portions can be smoothly lubricated by the oil scattered from the leaking depression 1 or the gap between the inner member 67 and the outer member 68. ~ Oil path 139~ As shown in Fig. 7, the pressure in the operating chamber 133 of the fourth clutch 66 and the pressure in the operating chamber 137 of the third clutch 70 are given and adjusted by the oil pump 14A. As shown in FIG. 7, an oil reservoir 99 is formed at the bottom of the crank chamber 35. The oil reservoir 99 is impregnated with a filter 141 as shown in Fig. 8. The filter i4i is connected to the oil pump 14〇. The oil stored in the oil reservoir 9 is sucked through the filter M1 by driving the oil pump 丨4〇. A pressure relief valve 147 is provided in the middle of the first oil passage 144. The sucked oil is cleaned by the oil cleaner I42 and is regulated to a specific pressure by the pressure relief valve 147. Thereafter, a portion of the purified oil is supplied to the sliding portion of the crankshaft 34 or the cylinder head 4〇. Further, a part of the purified oil is also supplied to the operation chamber 133 of the fourth disconnector 66 and the operation chamber 137 of the third clutch 7A. Specifically, the first oil path 144 extending from the oil cleaner 142 is connected to the second oil path 145 and the third oil path 14 and the second oil path 145 is passed from the valve 143 through the 134009.doc 30· 200928155 crankcase. The 32 side ' extends from the right end of the second rotating shaft 54 into the second rotating shaft 54. Then, the second oil path ία reaches the operation chamber 133. Therefore, oil is supplied to the operation chamber 133 via the second oil passage 145', and the pressure in the operation chamber 133 is adjusted. On the other hand, the third oil passage 146 extends from the valve 143 through the shifter cover 50 side 'from the left end portion of the second rotary shaft 54 to the second rotary shaft 54. Then, the third oil path 146 reaches the operating chamber 137. Therefore, oil is supplied to the operation chamber 137 via the third oil passage 146. A valve 143 is provided at a connection portion between the first oil passage 144, the second oil passage 145, and the third oil passage 146. The valve 143 opens and closes between the first oil passage 144 and the third oil passage 146 and opens and closes between the first oil passage 144 and the second oil passage diameter 145. At the valve 143, a motor 150 that drives the valve 143 is mounted as shown in FIG. The valve 143 is driven by the motor 150 to disconnect the third clutch 70 from the fourth clutch 66. In the present embodiment, the oil pump 14A, the valve ι43, and the motor 150 constitute an actuator 103 for applying a hydraulic pressure to the third clutch 7A and the fourth clutch 66 of the hydraulic clutch. Then, the actuator ι 3 is controlled by the ECU 138 shown in Fig. 6 to turn on/off (第n/OFF) the second clutch 70 and the fourth clutch 66. Specifically, the actuator 1A3 appropriately applies hydraulic pressure to the operation chamber 133 and the operation chamber 137, thereby disconnecting the third clutch 70 and the fourth clutch 66. More specifically, the throttle opening sensor 112 and the vehicle speed sensor 88 are connected to the ECU 13 8 as shown in Fig. 6 . The ECU 138 as the control unit controls the actuator based on at least one of the throttle opening degree detected by the throttle opening degree sensor 112 and the vehicle speed detected by the vehicle speed sensor 88. 134009.doc •31 - 200928155 103 ° In the present embodiment, the ecu 138 as the control unit is based on the throttle opening detected by the throttle opening sensor 112 and by the vehicle speed sensor. The vehicle speed detected by 88 is used to control the actuator 1〇3. Specifically, the ECU 13 8 applies the throttle opening degree output from the throttle opening degree sensor 112 and the output from the vehicle speed sensor 88 based on the v_n line diagram read from the memory n3. The information obtained by the vehicle speed is used to control the actuator 1〇3. Specifically, the valve 143 is formed in a substantially cylindrical shape. The valve 143 defines an internal path 148 for opening the first oil path 144 and the second oil path 145 to open the first oil path 144 and the third oil path internal path 149. The valve 143 is rotated by the motor 150 to select the first oil path 144 to be opened by the second oil path 145 and the first oil path 144 and the third oil path 146 by the internal paths 148, 149. In the open state, the first oil path 144 is connected to the third oil path 146 and on the other hand the first oil path 144 and the second oil path! 45 off the situation, and the first oil path 144 is disconnected from the third oil path 146 and the first oil path 144 and the second oil path 145 are also disconnected.

Any of the situations. Thereby, the state in which both the fourth clutch 66 and the third clutch 70 are disconnected, the state in which the fourth clutch 66 is connected and the third clutch 70 is off, or the fourth clutch 66 is off is selected, and the third clutch 66 is selected. Any of the states in which the clutch 70 is connected. - Action of the shifting device 31 - Next. Referring to Fig. 9 to Fig. 12, the crankshaft 34 (= input shaft 52) of the shifting device 31 is started to rotate, and the first speed is reached. First, if the engine 30 starts, 134009.doc 32·200928155 turns. The inner member 56 of the first clutch 55 rotates with the input shaft 52. Therefore, the rotational speed of the input shaft 52 is equal to or higher than the specific rotational speed (= first rotational speed), and when the inner member 56 starts to apply a centrifugal force of a specific magnitude or more, the first clutch 55 is turned on as shown in Fig. 9 . If the first clutch 55 is turned "on", the first shifting gear pair 86 will rotate together with the outer member 57 of the first clutch 55. Thereby, the rotation of the input shaft 52 is transmitted to the first rotating shaft 53. The fifth gear 87 rotates together with the first rotating shaft 53. Therefore, the first transmission gear pair 84 also rotates accompanying the rotation of the first rotating shaft 53. Therefore, the rotation of the first rotating shaft 53 is transmitted to the second rotating shaft 54 via the first transmission gear pair 84. The seventh gear 74 rotates together with the second rotating shaft 54. Therefore, the second transmission gear pair 85 also rotates accompanying the rotation of the second rotary shaft 54. Therefore, the rotation of the second rotary shaft 54 is transmitted to the third rotary shaft 64 via the second transfer gear pair 85. The thirteenth gear 79 rotates together with the third rotating shaft 64. Therefore, with the rotation of the third rotating shaft 64, the third transmission gear pair 98 also rotates. Therefore, the rotation of the third rotating shaft 64 is transmitted to the output shaft 33 via the third transmission gear pair 98. Thus, when the pedal type vehicle 1 is propelled, that is, at the first speed, as shown in FIG. 9, the first clutch 55, the first shift gear pair 86, the first transmission gear pair 84, and the second transmission gear pair are 85 and the third transmission gear pair 98, the rotation is transmitted from the input shaft 52 to the output shaft 33. The second gear 65 that is common to the fifth gear 87 at the time of the second speed is rotated by the same as the first shaft 153009.doc -33·200928155. Therefore, the third gear 62 engaged with the fourth gear 65 and the inner member 6 of the second clutch 59 are also rotated together. Therefore, if the rotational speed of the input shaft 52 rises, the rotational speed of the inner member 6 of the second clutch 59 also rises. When the rotational speed of the input shaft 52 becomes higher than the second rotational speed of the first rotational speed, the rotational speed of the inner member 6〇 also rises. As shown in FIG. 10, the second clutch 59 is turned on. • Here, in the present embodiment, the gear ratio of the second shift gear pair 83 is smaller than the gear ratio of the first shift gear pair 86. Therefore, the rotational speed ° of the fourth gear 65 is at the rotational speed of the second gear 63. Therefore, via the second shifting gear pair 83, the rotation is transmitted from the input shaft 52 to the first rotational axis. On the other hand, the rotation of the first rotating shaft 53 is not transmitted to the input shaft 52 by the one-way rotation transmitting mechanism %. The rotational force transmission from the first rotating shaft 53 to the output shaft 33 is the same as that of the first speed, and is performed via the first transmission gear pair 84, the second transmission gear pair 85, and the third transmission gear pair 98. Thus, at the second speed, as shown in FIG. 1A, the second clutch 59, the second shifting gear pair 83, the first transmission gear pair 84, the second transmission gear pair, and the third transmission gear pair 98 are rotated. It is transmitted from the input shaft 52 to the output shaft 33. When the speed of the crankshaft 34 (=the input shaft 52) is higher than the second rotation speed and the vehicle speed is equal to or higher than the specific vehicle speed, the valve 143 is driven as shown in FIG. The third clutch 7 is turned on. Therefore, the third shift gear pair 91 starts to rotate. Here, the gear ratio of the third shift gear pair 91 is 134009.doc -34 - 200928155 to the gear ratio of the second transmission gear pair 85. Therefore, the rotational speed of the tenth gear 77 of the third shift gear pair 9ι is higher than the rotational speed of the eighth gear 78 of the second transmission gear pair 85. Therefore, the rotation of the second rotating shaft 54 is transmitted to the third rotating shaft 64 via the third shifting gear pair 91. On the other hand, the rotation of the third rotation shaft 64 is not transmitted to the second rotation shaft 54 by the one-way rotation transmission mechanism. The rotation system of the second rotation shaft 64 is the same as the above-described idling speed and the second speed. The three transfer gear pair 98 is transmitted to the output shaft 33. Thus, at the third speed, as shown in FIG. u, via the second clutch 59, the second shifting gear pair 83, the first transmission gear pair 84, the third clutch 7〇, the third shifting gear pair 91, and the third transmission gear In the case of 98, the rotation is transmitted from the input shaft 52 to the output shaft 33 to the fourth speed. When the third speed is changed, if the rotational speed of the crank shaft 34 (= input shaft 52) is further changed and the vehicle speed is further increased, As shown in FIG. 12, the valve 143 is driven and the fourth clutch 66 is turned on. On the other hand, the third clutch 7 is turned off. Therefore, the fourth shift gear pair 9 〇 starts to rotate. Here, the gear ratio of the fourth shifting gear pair 90 is also smaller than the gear ratio of the second transmitting gear pair 85. Therefore, the rotational speed of the twelfth gear 76 of the fourth shift gear pair 90 is higher than the rotational speed of the eighth gear 78 of the second transfer gear pair 85. Therefore, the rotation of the second rotating shaft 54 is transmitted to the third rotating shaft 64 via the fourth shifting gear pair 9'. On the other hand, the rotation of the third rotary shaft 64 is not transmitted to the second rotary shaft 54 by the one-way rotary transfer mechanism 93. The rotation of the third rotating shaft 64 is the same as that of the above-described idling to third speed, and is transmitted to the output shaft 33 via the 134009.doc • 35· 200928155 third transmission gear pair 98. Thus, at the fourth speed, as shown in FIG. 12, via the second clutch 59, the shifting gear pair 83, the first transmission gear pair 84, the fourth clutch ", the first speed gear pair 9" and the second transmission gear pair 98, The rotation is transmitted from the input shaft 52 to the output shaft 33. As explained above, the present embodiment employs a so-called gear train type shifting device. Therefore, for example, compared to a stepless shifting device using a V-belt, energy is used. The transmission loss is less. As a result, the process of the vehicle can be improved. Especially in the case of the engine unit 2〇 of the present embodiment, when the engine unit with a long distance between the input shaft 52 and the output shaft 3 is used, In the case of a belt, the length of the V-belt becomes longer. Therefore, not only the stroke is particularly deteriorated, but also the problem of the V-belt springing is caused. Because of the "the so-called gear system described in the present embodiment The shifting device 31 is particularly useful for an engine unit having a long distance between the input shaft 52 and the output shaft 33. This embodiment is formed between the input shaft 52 and the first rotating shaft 53, and the second rotating shaft 54 and the second The structure of the three-speed rotating shaft between 64. Specifically The first shifting gear pair 86 and the second shifting gear pair 83 are disposed between the input shaft and the "rotating shaft 53. The third shifting gear pair 91 and the fourth shifting gear pair 90 are disposed on the second rotating shaft 54 and the third The rotation axis 64. Therefore, the configuration of the transmission device provided on a single rotating shaft can simplify the structure of the transmission device 3i compared to the use of an invariant device such as a planetary gear, and the transmission device can be miniature. Further, in the present embodiment, the fourth gear 65 of the second shift gear pair 83 is common to the fifth gear 87 of the first transmission gear pair 84. Therefore, the change is 134009.doc -36- 200928155 Further, in the present embodiment, the first rotating shaft 53 and the third rotating shaft 64' provided for shifting are used to perform the so-called gear train between the wheel input shaft 52 and the output shaft 33. The power transmission is carried out. Therefore, it is not necessary to provide another power transmission mechanism such as a key bar. In the case of advancement, it is not necessary to provide, for example, a key bar.

In the case of the If, it is also provided with a chain guide or a chain tensioner to suppress the chain bounce. Therefore, the structure of the shifting device 3 can be particularly simplified. In particular, the speed change device 31 can be miniaturized. In the present embodiment, the speed change device 31 is of the fourth speed. Therefore, compared with the three-speed shifting device, since the speed of the region in which the vehicle is used is large, the number of shifts is large. Therefore, it is easy to realize comfortable automatic shifting. In the present embodiment, the input shaft 52, the first rotating shaft 53, the second rotating shaft 54, the second rotating shaft 64, and the output shaft 33 are arranged in a direction perpendicular to the axial direction of the input shaft 52 (ie, the front-rear direction). Therefore, with respect to the axial direction of the input shaft 52, the shifting device 31 can be miniaturized. As a result, the width of the pedal ◎ type vehicle 1 in the vehicle width direction can be suppressed. Therefore, the inclination angle of the scooter type vehicle 1 can be largely determined. In particular, in the present embodiment, the upstream side clutch group 81 and the downstream side clutch group 82 are disposed at positions where at least a part of the input shaft 52 is axially overlapped. Therefore, for example, the width of the shifting device 31 with respect to the direction of the input shaft 52 can be further reduced as compared with the case where the upstream side clutch group 8 1 and the downstream side clutch group 82 do not overlap with respect to the drawing direction of the input pump 52. . As a result, the width of the pedal type vehicle 1 in the vehicle width direction can be further reduced. From the viewpoint of further reducing the width of the pedal type vehicle 1 in the vehicle width direction, the upstream side 134009.doc - 37 - 200928155 preferably overlaps the axial side clutch group 81 and the downstream side clutch group 82 of the input shaft 52. The four clutches 66 are configured in a stack' and, in terms of the second direction of departure, at least one of the inputs 31 with respect to the input shaft speed device 31, the first clutches 55 and L are substantially overlapping, and are in relation to the vehicle width direction.

In the present embodiment, at least a part of the recloser 59 and the third clutch 70 of the first clutch 55 and the first vehicle width direction are disposed to overlap each other with respect to the vehicle width portion. Therefore, the width in the axial direction of the shifting gear 52 can be further reduced. From the viewpoint of further reducing the width in the axial direction of the shaft 52, it is considered that the fourth clutch 66 is preferably disposed in the vehicle width direction and the second clutch 59 and the third clutch 7 are disposed to substantially overlap. Further, in the present embodiment, with respect to the axial direction of the input shaft 52, the first shift gear pair 86 and the fourth shift gear pair 9 are disposed at positions where at least a part of them overlap each other. The second shifting gear pair 83 and the third shifting gear pair (4) are disposed at positions where at least - portions overlap each other. Therefore, the width of the variable speed device 31 with respect to the axial direction of the input shaft 52 can be particularly reduced. Further, as in the present embodiment, the axis is used. ^. The input shaft 52, the first rotating shaft 53, the second rotating shaft 54, the third rotating shaft 64, and the output shaft % are arranged in a manner that the side faces on a substantially horizontal straight line, whereby the input shaft 52 can be compared with the input shaft 52. The distance between the output shafts 33. Moreover, by adjusting the arrangement of the axes C1 to C5, the distance between the input shaft 52 and the output shaft can be adjusted, for example, by making at least any one of the axes c1 to C5 deviate from the straight line by an adjustable adjustment. The distance between the input shaft 52 and the output pumping 33. For example, it is also conceivable to place the first shifting gear pair 86 with the first clutch 55 with the 134009.doc -38 - 200928155 on the right side and the fourth shifting gear pair 90 for the other. The fourth clutch 66 is disposed on the left side. Further, it is also conceivable that the second transmission gear pair 83 is disposed on the left side with respect to the second clutch 59, and the third transmission gear pair 91 is disposed on the right side with respect to the third clutch 70. In other words, it is also conceivable that the first transmission gear pair 86 and the fourth transmission gear pair 9 are disposed on opposite sides of each other for the first clutch 55 and the fourth clutch 66 arranged in the front-rear direction. The second clutch 59 and the third clutch 70' in the direction are disposed on the opposite sides of the second shift gear pair 83 and the third shift gear pair 91. However, in the case of such a configuration, the shifting device 3 is widened. The width is relatively large. With respect to the 'the present embodiment, the fourth shifting gear pair 90 is placed on the same side of the first shifting gear pair 86 as the first clutch 55 on the side with respect to the fourth clutch 66' Further, the third shift gear pair 9 丨 is positioned on the same side of the second shift gear pair 83 as the second clutch 59 on the side of the third clutch 70 ′, whereby the width of the shifting device 3 ′ in the vehicle width direction can be suppressed. In the case of the first clutch 55 and the fourth clutch 66' arranged in the front-rear direction, the first shift gear pair 86 and the fourth shift gear pair 90 are disposed on the same side of each other' and are arranged in the front-rear direction. The second clutch 59 and the second clutch 70' are disposed on the same side of the second shift gear pair 83 and the third shift gear pair 91 to reduce the width in the vehicle width direction of the shifting device 31. Further, the vehicle of the shifting device 31 is further suppressed. The viewpoint of the width in the width direction is considered to be such that the plurality of clutches arranged on the same rotating shaft are adjacently arranged. Specifically, S 'should be as in the present embodiment, in the first shifting gear pair 86 and the second variable 134. 009.doc -39- 200928155 Speed gear pair 83, the first clutch 55 and the second clutch 59β are disposed between the second shift gear pair 91 and the fourth shift gear pair 9〇, and the third clutch 70 and the fourth clutch are disposed. 66. For example, the third clutch 7A and the fourth clutch 60 may be configured by a centrifugal clutch. In this case, for example, when the third clutch 7 is lower than the fourth clutch at the second rotating shaft 54, the rotation speed is lower. In the case of the opening, the fourth clutch 66 cannot be connected and the third clutch 70 is opened. Therefore, in order to turn the third clutch 7 〇 and the fourth clutch 66 into contact, the fourth The transmission gear pair 9 turns the power transmission between the second rotating vehicle 54 and the third rotating shaft 64, and a one-way clutch or a one-way gear must be provided. Therefore, the structure of the shifting device 31 tends to be complicated. With respect to this, in the present embodiment, the third clutch 70 and the fourth clutch 66 are constituted by hydraulic clutches. Therefore, the third clutch 7 〇 and the fourth clutch 66 can be freely disconnected. Therefore, it is not necessary to additionally provide a one-way clutch or a one-way gear. Therefore, the structure of the shifting device 31 can be more simplified. <<Embodiment 2>> In the above-described embodiment, a pedal type vehicle i is exemplified as an example of a suitable embodiment for carrying out the invention. However, in the present invention, the motorcycle is not limited to the pedal type vehicle. In the present embodiment 2, an example of a suitable mode for carrying out the invention will be described by way of an example of a so-called light-duty treadmill 2. Further, in the description of the present embodiment 2, members having a common function are described by the same reference numerals as those of the above-described embodiment. Referring to FIG. 4, FIG. 7, and FIG. 9 to FIG. 12 in common with the above-described embodiment. (Schematic structure of the light motorcycle treadmill 2) 134009.doc -40- 200928155 First, the schematic structure of the light motorcycle treadmill 2 will be described with reference to Figs. 13 and 14 . Further, in the following description, the directions of the front, rear, left, and right directions refer to the direction of the rider riding on the seat cushion 14 of the light motorcycle treadmill 2. As shown in FIG. ,, the light motorcycle treadmill 2 is provided with a vehicle body frame 1 (). The body frame 1 has a head pipe (not shown). The head tube is attached to the front of the vehicle with the part facing downwards - 彳 slightly inclined to extend forward. A handle 12 is provided at an upper end of the head pipe. On the other hand, the front end 15 is connected to the lower end of the head pipe. The front wheel 15 is rotatably mounted as a driven wheel front wheel 16 at the front and lower 15 ends. ° The body cover 13 is attached to the body frame Π). Part of the body frame ig is covered by the body cover 13. The seat cover 13 is mounted with a rider seat 14 and is mounted on the body frame with a side stand 23 at the approximate center of the vehicle. The engine unit 20 is suspended from the body frame 10. In the present embodiment, the engine f-unit 20 is fixed to the body frame. In summary, the engine unit 2() is a so-called solid-type engine unit. The engine unit 20 of the present embodiment 2 is of a type in which the front and rear sides are shorter than the type in which the engine unit of the above-described embodiment is long in the front-rear direction. Specifically, the shifting device 31 of the engine unit 2 of the above-described embodiment 1 is a type in which the distance between the input shaft 52 and the output shaft 33 is longer, and the shifting of the engine unit 20 of the present embodiment 2 The device 31 is of a type in which the distance between the input shaft 52 and the output shaft 33 is short. Therefore, the engine unit 20 of the present embodiment 2 is particularly useful for a light-duty treadmill or off-road vehicle, a road vehicle, and the like which require higher kinetic performance than a scooter type vehicle. The arm frame 28 is attached to the rear body frame ίο. The rear arm 28 can be rocked about the cymbal shaft 25. At the rear end of the rear arm 28, 134009.doc •41 - 200928155 is rotatably mounted as the rear wheel 18 of the swaying wheel. The rear wheel 18 is coupled to the output shaft 33 of the transmission 31 by a power transmission mechanism (not shown). Therefore, the rear wheel 18 is driven by the engine unit 20. Further, one end of the pad unit 22 is attached to the rear end of the rear arm 28. The other end of the pad unit 22 is attached to the vehicle body frame 1A. The rocking of the rear arm 28 is suppressed by the weir unit 22. As shown in Fig. 4, in the present embodiment, a vehicle speed sensor 88 is provided for the output shaft 33. Specifically, the vehicle speed sensor 88 is provided for the fourteenth gear 80 that rotates together with the output shaft 33. However, the vehicle speed sensor 88 may be provided for a rotating shaft other than the output shaft 33 © or for other members that rotate with respect to the output shaft 33 at a constant number of revolutions. (Structure of Engine Unit 20) FIG. 16 is a cross-sectional view of the engine unit 2A. Fig. 4 is a schematic view showing the structure of the engine unit 2''. As shown in Fig. 16, the engine unit 2 is provided with an engine 3 and a speed change device 31. Further, this embodiment 2 describes an example in which the engine 3 is a single-cylinder engine. However, in the present invention, the engine 3 is not limited to a single cylinder engine. The engine 30 can also be a multi-cylinder engine such as a 2-cylinder engine. - Engine 30 The engine 30 includes a crankcase 32, a rainbow body 37, a cylinder head 4A, and a crankshaft. Inside the crankcase 32, a crank chamber 35 is defined. A cylinder 38 is formed in the inner portion of the cylinder 37 to define an opening in the crank chamber 35. A cylinder head 40 is attached to the front end of the cylinder block. A crank shaft 34 extending in the vehicle width direction is disposed in the crank chamber 35. A link % is attached to the crank shaft 34. The front end of the joint (four) is mounted on the cylinder 38. The inner piston 39 is divided into a cylinder head by the piston 39, the cylinder 37 and the red head 4〇, and the front part of the ignition part is located at 134009.doc • 42· 200928155 combustion chamber 41. The fire plug 42. Fig. 17 is a partial cross-sectional view showing the engine unit 20 of the foot starter 1 and the battery motor 101. As shown in Figs. 14 and 17, the engine unit 2 is provided with a pedal. The starter 1 〇〇. The rider of the light machine treadmill 2 can start the engine 30 by operating the kick starter 100. The kick starter 100 has a foot pedal 24. The foot pedal 24 is as shown in Fig. 14. As shown, the rear side of the crankshaft 34 and the lower side are disposed on the right side of the crankcase 32. The footrest 24 is mounted on the pedal shaft 1〇2 ^The compression coil spring is disposed between the pedal shaft 1〇2 and the crankcase 32. 103. The compression coil spring 1〇3 is given a reverse rotation to the pedal shaft 102 that is rotated by the rider's operation. The direction of the force is applied to the pedal shaft 102. On the other hand, the gear 1 is rotatably provided on the shaft 105. The gear 1〇4 is engaged with the gear 106. Via the gear 104, etc. The rotation of the pedal shaft 102 is transmitted to the crankshaft 34. The gear 1〇6 is engaged with the gear 123 provided on the shaft 127. Therefore, the rotation of the gear 104 is transmitted to the shaft 127 via the gear 106 and the gear 123. A gear 124 is disposed on the shaft 127. The gear 124 is engaged with the gear 125 disposed on the crankshaft 34. Therefore, the rotation of the shaft 127 is transmitted to the crankshaft 34 via the gear 124 and the gear 125. Therefore, by the rider The crankshaft 34 is operated to rotate the crankshaft 34. Further, the engine 30 is also provided with a battery cell motor 1〇1. The battery cell motor 101 is mounted to the crankcase 32. The rotation of the battery cell motor 1〇1 is via The gears 120, 121 and 126 are transmitted to the crankshaft 34. Thereby, the battery cell 101 is driven by the operation of the rider, whereby the engine 30 is started. - Balancer shaft 115-134009.doc • 43- 200928155 As shown in FIG. 16, the engine 30 is provided with a balancer shaft 11 A balancer 115A is provided with a gear 118. The gear 118 is engaged with a gear 119 provided on the crankshaft 34. Therefore, the balancer shaft 115 rotates together with the crankshaft 34. As shown in Fig. 16 and As shown in Fig. 15, the axis of the balancer shaft 115 is disposed near the axis C2 of the second rotating shaft 54. As shown in Fig. 16, when viewed from the axial direction of the first rotating shaft 53, the first rotating shaft 53, the second gear At least a portion of the ninth gear 87 and at least a portion of the balancer U5A are configured to overlap each other. Here, the balancer shaft 115 is specifically disposed to overlap at least a portion of the first rotating shaft 53 when viewed in the axial direction of the first rotating shaft 53. The balancer shaft 115 is located in the vehicle width direction, and the link is connected to the crankshaft 34. The first rotary shaft 53 is located on the right side with respect to the vehicle width direction. The balancer shaft 115 is offset from the first rotating shaft 53 in the vehicle width direction. In other words, the balancer shaft 115 and the first rotating shaft 53 are arranged so as not to overlap each other with respect to the vehicle width direction. - Generator 45 - As shown in Figures 16 and 17, a generator cover 43 is attached to the left side of the crankcase 32. The generator chamber 44 is formed by the generator cover 43 and the crankcase. The left end of the crankshaft 34 projects from the crank chamber 35 and reaches the generator chamber 44 in the generator 44, on the crankshaft 34. A generator 45 is attached to the left end. The generator 45 is provided with an inner member 45&amp; and an outer member 45b. The inner member 45&amp; 2 is non-rotatably mounted to the crankcase 32. On the other hand, the outer member is priced at the crankshaft 34. The left end portion. The outer member 45b rotates together with the crank shaft 34. Therefore, if the crank shaft 34 rotates, the outer member 45b relatively rotates with respect to the inner member 134009.doc 44· 200928155 45a. Thereby, power generation is performed. On the right side, a shifting device cover 5 is attached. The shifting device cover 50 and the crank case 32 are divided to form a shifting device 51 located on the left side of the crankcase 32. - Structure of the shifting device 31 - Next 'Main reference drawing 4, the configuration of the shifting device 31 will be described in detail. The shifting device 31 is provided with a four-speed automatic transmission of the input shaft 52 and the output shaft 33. The shifting device 31 is a so-called gear type type shifting device. Via complex The plurality of shifting gear pairs transmit power from the input shaft 52 to the output shaft 33. The right end portion of the crank shaft 34 protrudes from the crank chamber 35 and reaches the shifting device chamber 51. The crank shaft 34 doubles as the input shaft 52 of the shifting device 31. The shaft structure - the shifting device 31 has a first rotating shaft 53, a second rotating shaft 54, a third rotating shaft 64, and an output shaft 33. The first rotating shaft 53, the second rotating shaft 54, the second rotating shaft 64, and the output shaft 33 are arranged in parallel with the input shaft 52. The symbols C1, C2, C3, C4, C5 of Fig. 15 indicate the axis of the input shaft 52, the axis of the first rotary shaft 53, the axis of the second rotary shaft 54, The axis of the third rotating shaft 64 and the axis of the output shaft 33. As shown in Fig. 15, all the rotating shafts of the input shaft 52, the first rotating shaft 53, the second rotating shaft 54, and the third rotating shaft 64 are configured as In other words, the input shaft 52, the first rotating shaft 53, the second rotating shaft 54, and the third rotating shaft 64 are the axis C1 of the input shaft 52, the axis C2 of the first rotating shaft 53, and the second. The axis C3 of the rotating shaft 54 and the axis C4 of the third rotating shaft 64 are arranged to be 134009 on the side .doc -45- 200928155 is rectangular. As shown in Fig. 15, at least one of the axis C2 of the first rotating shaft 53 and the axis C4 of the third rotating shaft 64 is not located on the axis C1 including the input shaft 52 and the second rotating shaft. In the plane P of the axis C3 of 54. In detail, the axis C2 with respect to the first axis of rotation 53 is located on one side with respect to the plane P, and the axis C4 of the third axis of rotation 64 is located on the other side with respect to the plane p. Specifically, the axis C2 with respect to the first rotation axis 53 is located on the upper side with respect to the plane P, and the axis C4 of the third rotation axis 64 is located on the lower side with respect to the plane p. Therefore, the axis of the first rotating shaft 53 is clamped to the upper side, and the third rotating shaft 64 is located at the lower side. The axis C4 of the third rotating sleeve 64 is located forward of the axis C3 of the second rotating shaft 54 with respect to the front-rear direction. In detail, the axis C4 of the third rotating shaft 64 is located between the axis 第二 of the second rotating shaft 54 and the axis C1 of the input shaft 52 with respect to the front-rear direction. The axis C5 of the output shaft 33 is as shown in Fig. 15 and is located above and behind the axis C4 of the third rotating shaft 64. The axis C5 of the output shaft 33 is viewed from the side φ to be located on the axis C1 of the input shaft 52, the axis C2 of the first rotating shaft 53, the axis C3 of the second rotating shaft 54, and the axis of the third rotating shaft 64. The line is outside the imaginary rectangle formed by the line. The axis C5 of the output shaft 33 is viewed from the side as being rearward than the axis C3 of the second rotary shaft 54. Further, the plane P extends rearward and upward. In summary, the axis C3 of the second rotating shaft 54 is at a higher position than the axis ci of the input shaft 52. Further, in the second embodiment, an example in which the output shaft 33 and the third rotating shaft 64 are separately provided will be described. However, the present invention is not limited to this structure. Transmission 134009.doc -46- 200928155 The output shaft 33 and the second rotation shaft 64 are common. In other words, the rear wheel 18 can be attached to the third rotating shaft 64. ~Upstream clutch group 81~

上游 As shown in Figs. 16 and 4, the upstream side clutch group 81 is provided on the input shaft 52. The upstream clutch group 81 includes a first clutch 55 and a second clutch. The first clutch 55 is disposed on the right side of the second clutch 59. The first departure. The 55 and the second clutch 59 are each constituted by a centrifugal clutch. Specifically, in the present embodiment 2, the first clutch 55 and the second clutch 59 are respectively constituted by a drum type centrifugal clutch. However, the present invention is not limited to this structure. The clutch 55 and the first clutch 59 may be clutches other than the centrifugal clutch. For example, the first clutch 55 and the second clutch 59 may be hydraulic clutches. Among them, the first clutch 55 is preferably a centrifugal clutch. The first clutch 55 is provided with an inner member "as an input side clutch member" and as an output (four) joint member outer structure #57. The inner member % is provided so as not to be rotatable with respect to the input shaft 52. Therefore, the inner member % is coupled to the input shaft The rotation of 52 - the same rotation - in other respects, the outer member 57 can be rotated about the input shaft 52. = the rotational speed of the oil is greater than the specific rotational speed, due to the centrifugal force acting on the member 56, the inner member 56 and the outer member 57 In this case, the := device 55 will be turned on. On the other hand, when the inner member_outer member 57 = rotates, 'if the rotation speed is less than the special (four) rotation speed, the distance is::: the centrifugal force of the inner cymbal 56 When the inner member 56 is separated from the outer member 57, the first clutch 55 is disengaged. The first clutch 59 is provided as an output side and cooperates as a wheel-in side clutch member outer member 61. The inner member 60 of the member is attached. The member 60 and the third gear 62 of 134009.doc-47-200928155 described later are not rotatably provided. If the input shaft 52 rotates, the rotation is via the first shifting gear pair 86, the first rotating shaft 53, and the second shifting gear pair. 83 and pass The inner member 6〇β thus rotates the inner member 6 together with the rotation of the input shaft 2. The outer member 61 can rotate with respect to the input shaft 52. If the rotational speed of the input shaft 52 is greater than a specific rotational speed, it acts on the inner member (10) Centrifugal force 'The inner member 60 comes into contact with the outer member 61. Thereby, the second clutch 59 is turned on. On the other hand, if the inner member 6〇 is rotated in the state in which the outer member 61 is turned on, if the rotation speed is When the rotation speed is less than the specific rotation speed, the centrifugal force acting on the inner member 60 becomes weak, and the inner member 6 is separated from the outer member 6. Thus, the second clutch 59 is disconnected. Further, in the present embodiment 2, the outer member 57 The outer member 61 is formed of the same member. However, the present invention is not limited to this configuration. The outer member 57 and the outer member 61 may be configured by different members. The rotational speed and connection of the input shaft 52 when the first clutch 55 is connected The rotational speeds of the input shafts 52 when the second clutch 59 is present are different from each other. In other words, the rotational speed of the inner member 56 when the first clutch 55 is connected and the rotational speed of the inner member 60 when the second clutch 59 is connected are mutually Specifically, the rotational speed of the input shaft 52 when the first clutch 55 is connected is lower than the rotational speed of the input shaft 52 when the second clutch 59 is connected. More specifically, the first clutch 55 is coupled to the input shaft 52. When the rotation speed is equal to or higher than the first rotation speed, the first clutch 55 is in the OFF state when the rotation speed of the input shaft 52 is smaller than the first rotation speed. The second clutch 59 is connected to the input shaft. When the rotation speed of 52 becomes higher than the second rotation speed of the first rotation speed, the second clutch 59 134009.doc -48- 200928155 is rotated at the input shaft 52 to be smaller than the second rotation speed. When 'becomes disconnected state' Ο

The member 57 is external to the first clutch 55, and the first gear 58 is non-rotatably disposed to the outer member 57. The first gear 58 rotates with the outer member 57 of the first clutch 55. On the other hand, a second gear 63 is provided on the first rotating shaft 53. The second gear 63 meshes with the first gear 58. The first gear "and the first gear 63 are formed by the first shift gear pair 86. In the present embodiment, the first shift gear pair 86 constitutes a first speed shift gear pair. The second gear 63 is a so-called one-way gear. Specifically, the second gear train transmits the rotation of the first gear 58 to the first rotating shaft 53. On the other hand, the second gear 63 does not transmit the rotation of the first rotating shaft 53 to the input shaft 52. The second gear 63 has both the one-way rotation transmission mechanism %. As the inner member 6 of the output side clutch member of the second clutch 59, the third gear 62 is recognized. The third gear 62 is the same as the inner member 60. On the other hand, the fourth rotating shaft 53 is provided with a fourth gear 65. The 65 series meshes with the third gear 62. The fourth gear "and the third gear 盥: the second shifting gear pair 83 constitutes a second shifting gear pair 83 It has a different gear ratio than the first and second. With the second gear shift pair 83 having a gear ratio smaller than that of the first shift gear pair 86, the pair 83 constitutes the second speed shift gear pair. First-variable gears The first clutch 55 and the second clutch 59 are located between the 86th and the second shifting gears, and the second clutch is changed to the second clutch::: between the above-mentioned third and third. The variable gear (10) and the second variable gear pair 134009.doc -49 - 200928155 = the real gear 65 are also provided as the fifth _, the fourth gear 65 and the fifth gear 87 are rotated. The shaft 54 and the sixth gear 75 are for the second: 嗖詈. The mountain is also non-rotatable from the ash sleeve 54. The eighth gear 75 is coupled to the second rotating shaft 54. The fifth gear 87 is the same as the first '&quot;, and has the function of the fourth gear 65: the gear 75 is engaged. The wheel 75 constitutes the first transmission gear pair. The wheel 87 and the sixth tooth ❹ rotation=the rotation gear 74 are unable to sigh the seventh gear 74 and the second rotation station _ aspect 'the third rotation axis 64, the eighth gear 2 is red for the second rotation shaft 54 : The first three rotating shafts are not rotatably arranged: the eighth gear 74 and the eighth gear 78 are connected together with the eighth tooth (four) to form a second transmission gear pair... the seventh gear 74 and Toward the gear, specifically, the eighth gear (four) shaft 54 is transmitted to the third rotating shaft. (4) The wheel does not transmit the rotation of the third rotating shaft 64 to the second shaft. However, the second: the alum 78 has a one-way rotation transmitting mechanism. For example, the eighth tooth (four) is a pass Μ wheel and does not have to be a so-called one-way gear. Example. In other words, the seventh gear 74 can be a so-called green gear. Specifically, the second = 4 has both the one-way rotation transmission mechanism and the eighth gear 78, and the rotation of the second rotation shaft 54 is transmitted by the second rotation shaft 54. The rotation of the eighth gear 78 is transmitted to the first to downstream side clutch groups 82 to 134009.doc -50 - 200928155. The second rotation shaft 54 is provided with the downstream side clutch group 82. The downstream side clutch group 82 is located after the upstream side clutch group 81. square. As shown in Fig. 16, the downstream side clutch group 82 and the upstream side clutch group 81 are disposed at positions where at least a part of the input shaft 52 is axially overlapped. In other words, the downstream clutch unit 82 and the upstream clutch group 81 are disposed at positions where at least a portion overlaps with respect to the vehicle width direction. Specifically, the downstream side clutch group 82 and the upstream side clutch group 8 are disposed at positions substantially overlapping with respect to the vehicle width direction.

The downstream side clutch group 82 includes a third clutch 70 and a fourth clutch 66. The fourth clutch 66 is disposed on the right side of the third clutch 70. Therefore, the direction in which the first clutch 55 is located with respect to the second clutch 59 is equal to the direction in which the fourth clutch 66 is positioned for the third clutch 70. Then, as shown in the figure, the first clutch 55 and the fourth clutch 66 are arranged to overlap at least partially with respect to the vehicle width direction. In other words, the first clutch 55 and the fourth clutch 66 are configured to be related to the input shaft 52. In the axial direction, at least a part of the reforming. The second aspect 59 and the third clutch 7 are configured to at least partially overlap with respect to the vehicle width direction. In other words, the second clutch 59 and the third clutch The 70 series are configured to at least partially overlap with respect to the axial direction of the input shaft 52. Specifically, the first clutch 55 and the fourth clutch are configured to be substantially weighted with respect to the vehicle width direction. In the __ aspect, the second clutch 59 and the third clutch 7G are each disposed to substantially overlap with respect to the vehicle width direction. The third clutch 1170 and the fourth clutch 66 are respectively constituted by so-called hydraulic clutches. Specifically, In the present embodiment 2, the third clutch 7〇 and the 134009.doc 51 200928155 four clutches 66 are respectively constituted by a disc type hydraulic clutch. However, the present invention is not limited to this configuration. The fourth clutch 66 and the three The clutch 7〇 may also be a clutch other than the hydraulic clutch. For example, the fourth clutch 66 and the third clutch 70 may also be centrifugal clutches, but the fourth clutch 66 and the third clutch 70 are preferably hydraulic clutches. In this manner, the first clutch 55, the second clutch 59, the fourth clutch, and the third clutch 7G are each a drum type or a disc type centrifugal clutch, or a drum type or a disc type hydraulic clutch. The clutch 55, the second clutch 59, the fourth clutch 66, and the third clutch 7 are all centrifugal clutches, and the first clutch 55, the second clutch 59, the fourth clutch 66, and the third clutch 70 are all hydraulic clutches. Moreover, the gears of the first clutch first clutch 59, the fourth clutch 66 and the third clutch 70 are relatively large or one of the plurality of clutches is centrifugal 'clutch H, and the other gears are hydraulically compared. The clutch may also be. Specifically, only the first clutch 55 is a centrifugal clutch, and the other clutches 59, 66, 70 may be hydraulic clutches. Conversely, the silver clutch of the younger clutch 55, The clutch 59, the fourth clutch 66, and the third y-mouth 70 have a relatively large gear or a plurality of clutches. The hydraulic clutch is also a hybrid H. The outer wheel is relatively small. The third clutch 7〇 is connected with the rotation speed of the fourth clutch 54. In other words, the rotation speeds of the second shafts 54 are connected to each other and the fourth clutch is connected: (4) The rotation speed of 71 is the same. (4), the connection (4) __ member 67 (4) The speed of the mutual rotation is 70 when the second rotation shaft 54 is 134009.doc -52- 200928155 The rotation speed of the second rotation shaft 54 of the four clutch 66 Below the connection has a first speed. = Clutch H70 is available as the input side clutch member ❹

Turn the ground 6 again. Therefore, the inner member 71 rotates together with the second rotational rotation. On the other hand, the outer member 72 is rotatable about the second rotating shaft 54. When the third clutch (54) is not turned on and the second rotary pump 54 is rotated, the inner member 71 rotates together with the second rotation (four), and the outer member 72 does not rotate with the second rotary shaft 54. In a state where the third clutch 70 is turned on, both the inner member 71 and the outer member 72 rotate together with the second rotating shaft 54. A ninth gear 73 is attached to the output side clutch member outer member 72 as the third clutch 70. The ninth gear 73 rotates together with the outer member 72. On the other hand, in the second rotating shaft 64, the tenth gear 77 is non-rotatably provided to the third rotating shaft 64. The tenth gear 77 is rotated together with the third rotating shaft. The ninth gear 73 and the tenth gear 77 are engaged with each other. Therefore, the rotation of the outer member 72 is transmitted to the third rotating shaft 64 via the ninth gear 73 and the tenth gear 77. The ninth gear 73 and the tenth gear 77 constitute a third shift gear pair 91. The gear ratio of the third shift gear pair 91 to the first shift gear pair 86, the gear ratio of the second shift gear pair 83, and the gear ratio of the fourth shift gear pair 90 have different gear ratios. The third shifting gear pair 91 is for the third clutch 70 on the same side of the second shifting gear pair 83 with respect to the second clutch 59. Specifically, 134009.doc •53· 200928155, the third shifting gear pair 91 is located on the left side with respect to the third clutch 7〇. Similarly, the first shifting gear pair 83 is located on the left side with respect to the second clutch 59. Further, the third shift gear pair 91 and the second shift gear pair 83 are arranged such that at least a part of them overlap each other with respect to the vehicle width direction. In other words, the third shift gear pair 91 and the second shift gear pair 83 are disposed with respect to the axial direction 5 of the input shaft 52, and at least a portion overlaps each other. Specifically, the third shift gear pair 91 and the second shift gear pair 83 are arranged to substantially overlap with respect to the vehicle width direction. The fourth clutch 66 includes an inner member 67 as an input side clutch member and an output side clutch member outer member 68. The inner member 67 is rotatably provided to the second rotating shaft 54. Therefore, the inner member 67 rotates together with the rotation of the second rotary shaft 54. On the other hand, the outer member 68 is rotatable about the second rotating shaft 54. When the fourth rotating shaft 54 is not turned on, if the second rotating shaft 54 rotates, the inner member 67 rotates together with the second rotating shaft, and the outer member 68 does not rotate together with the second rotating shaft 54. In a state where the fourth clutch 66 is turned on, the inner member 67 and the outer member "both sides rotate together with the second rotating shaft 54. A tenth-gear 69 is attached to the output side clutch member outer member 68 as the fourth clutch 66. The eleventh gear 69 is rotated together with the outer member (9). On the other hand, on the third rotating shaft 64, the twelfth gear 76 is rotatably provided to the third rotating shaft 64. The twelfth gear % is rotated in the same manner as the third rotating shaft 64. The eleventh gear 69 and the twelfth gear are engaged with each other. Therefore, the rotation of the outer member 68 is transmitted to the third rotating shaft 64 via the eleventh gear 69 and the twelfth gear 76. I34009.doc -54· 200928155 The eleventh gear 76 and the eleventh gear 69 constitute a fourth gear shift pair 90 齿轮 a fourth gear shift pair 90 is a gear ratio of the first shift gear pair 86, a gear ratio of the shift gear pair 83, and a gear ratio The gear ratio of the three shifting gear pair 91 has different gear ratios. The above-mentioned first touch: the human one clutch 70 and the fourth clutch 66 are located between the third shifting gear pair 91 and the fourth and fourth shifting gear pair 90. In other words, the third The clutch 70 and the fourth clutch 99 / γ / r / 4. σ 66 are disposed between the third shift gear pair 91 and the fourth shift gear pair 90.

❹ The fourth shifting gear pair 9 is for the fourth clutch 66 on the same side of the first shifting gear pair 86 on the side where the first clutch 55 is located. Specifically. The fourth shifting gear pair 90 is located on the right side with respect to the fourth clutch 66. Similarly, the first shifting gear pair 86 is located on the right side with respect to the first clutch 55. Further, the fourth shift gear pair 9 〇 and the first shift gear pair 86 are arranged such that at least a part of them overlap each other with respect to the vehicle width direction. In other words, the fourth shifting gear pair 9G and the first shifting gear pair 86 are arranged with respect to the axial direction 5 of the input shaft 52, at least a portion of which overlap each other. Specifically, the fourth shift gear pair 90 and the first shift gear pair 86 are arranged to substantially overlap with respect to the vehicle width direction. On the third rotating shaft 64, the thirteenth gear 79 is disposed in a non-rotatable manner with respect to the third rotating shaft. The thirteenth gear 79 is disposed in the vehicle width direction, and is rotated in the same manner as the twelfth gear 79 and the tenth gear 77, the thirteenth gear 79, and the third rotating shaft 64. On the other hand, on the output shaft 33, the fourteenth gear 80 is rotatably provided to the output shaft 33. In other words, the fourth gear 80 rotates together with the output shaft 33. The third transmission gear 98 is constituted by the fourteenth gear 134009.doc • 55· 200928155 1 8.3: wheel: 9. The rotation of the second rotation shaft 64 by the third transmission tooth is transmitted to the output shaft 33. ～Detailed configuration of the downstream side clutch group 82 to the keeper&apos; Mainly referring to Fig. 18, the downstream side clutch group 82° is described in detail. ” The third clutch 7G is provided with plates and 6. The plate group 136 has a plurality of friction plates 134 and a plurality of clutch plates 135. The plurality of friction plates 134 and the plurality of clutch plates 135 are laminated in the vehicle width direction in a mutually different manner. The friction plate 134 is not rotatable for the ^ (four) member 72. On the other hand, the clutch plate 135 is not rotatable to the inner member 71. The inner member 71 can be rotated with respect to the outer member 72. A stress plate 163 is disposed on the opposite side of the inner member 71 from the outer member 72 in the vehicle width direction. The stress plate μ] is biased by the compression coil spring 92 to the right side in the vehicle width direction. That is, the stress plate 163 is biased toward the hub portion ι62 side by the compression coil spring 92. An operation chamber 137 is defined between the hub portion 162 and the stress plate 163. • The operation chamber 137 is filled with oil. When the hydraulic pressure in the operation chamber 137 becomes high, the stress plate 163 is displaced in a direction away from the hub portion 162. Thereby, the distance between the stress plate 163 and the inner member 71 becomes short. Therefore, the plate group 136 is in a state of being pressed against each other. As a result, the inner member 71 and the outer member 72 rotate together, and the third clutch 70 is in a connected state. On the other hand, when the pressure in the operation chamber 137 is lowered, the stress chamber M3 is displaced toward the hub portion 162 side by the compression coil spring 92. Thereby, the crimping state of the plate group 136 is released. As a result, the inner member 71 and the outer member 72 can rotate together to open the third clutch 70. 134009.doc -56- 200928155 - In addition, although the third clutch 7Q is omitted, a leaky hole that communicates with the operation to U7 is formed. Moreover, the inner member η and the outer member π are not sealed. Thereby, when the clutch 70 is opened, the oil in the operating chamber can be quickly discharged. Therefore, according to this embodiment, the reactivity of the clutch 70 can be improved. On the other hand, according to the present embodiment, the oil can be smoothly slid by the oil leaking from the gap or the gap between the inner member 7 and the outer member 72. A plate group 132 is provided to the fourth clutch 66. The plate group 132 includes a plurality of friction plates 130 and a plurality of clutch plates 131. The plurality of friction plates 13A and the plurality of clutch plates 131 are laminated in the vehicle width direction in a mutually different manner. The friction plate 130 is not rotatable to the outer member 68. On the other hand, the clutch plate 131 is not rotatable to the inner member 67. The inner member 67 is rotatable to the outer member 68 and displaced in the vehicle width direction. A stress plate 161 is disposed on the opposite side of the inner member 67 from the outer member 68 in the vehicle width direction. The stress plate 161 is biased to the left side in the vehicle width direction by the compression coil spring 89. That is, the stress plate 161 is biased toward the hub portion 162 by the compression coil spring 89. An operation chamber 133 is defined between the hub portion 162 and the stress plate 161. The operating chamber 13 3 is filled with oil. When the hydraulic pressure in the operation chamber 13 3 is increased, the stress plate 161 is displaced in a direction away from the hub portion 162. Thereby, the distance between the stress plate 161 and the inner member 67 becomes short. Therefore, the plate group 132 is pressed against each other. As a result, the inner member 67 and the outer member 68 rotate together, and the fourth clutch 66 is in a connected state. On the other hand, if the pressure in the operation chamber 133 is low, the stress chamber 161 is 134009.doc -57 - 200928155 and is compressed by the compression coil spring 89 toward the hub portion 162 side, thereby releasing the crimping state of the plate group 132. . As a result, the inner member 67 and the outer member μ can rotate together to open the fourth clutch 66. Further, although the illustration is omitted, the fourth clutch 66 is formed with a small leak hole that communicates with the operation chamber 133. Moreover, the inner member 67 and the outer member μ are not sealed. Thereby, the oil in the operation chamber Π3 can be quickly discharged when the clutch 66 is off (four). Therefore, according to the present embodiment, the reactivity of the clutch 66 can be improved. Further, according to the present embodiment, the other sliding portions can be smoothly lubricated by the oil scattered from the upper side of the gap and the inner member 67 and the outer member. ~ Oil path 139~ As shown in Fig. 7, the pressure in the operating chamber 133 of the fourth clutch 66 and the pressure in the operating chamber 137 of the third clutch 70 are given by the oil pump 14 (). As shown in FIG. 7, an oil reservoir 99 is formed at the bottom of the crank chamber 35. The oil reservoir 99 is immersed in the accumulator 14 and the ferrator 141 is connected to the oil pump 14. The oil pump 14 is sucked up by the driving oil pump 14 〇' to store the oil stored in the oil reservoir 99. • A pressure relief valve 147 is provided in the middle of the first oil passage 144. The sucked oil is purified by the oil cleaner 142 and is regulated to a specific pressure by the pressure relief valve 147. Thereafter, a portion of the purified oil is supplied to the sliding portion of the crankshaft 34 or the cylinder head 4〇. Further, a part of the purified oil is also supplied to the operation chamber 133 of the fourth clutch f 66 and the operation chamber 137 of the third clutch 7〇. Specifically, a second oil path 145 and a third oil path are connected to the first oil path 144 extending from the oil cleaner 142. The second oil path extends from the right end of the second rotating shaft 54 to the second rotating shaft 54 from the valve 143 via the 134009.doc -58 - 200928155 shifting device cover 50 side. Then the second oil path 145 reaches the operating room (1). Therefore, oil is supplied to the operation chamber 133 via the second oil passage 145, and the pressure in the operation chamber 133 is adjusted. On the other hand, the third oil path 146 extends from the left end of the first rotating shaft 54 to the second rotating shaft 54 from the valve (4) through the crank phase 32 side. The 'third oil path 146' then reaches the operating chamber 137. Therefore, oil is supplied to the operation chamber 137 via the third oil passage 146. ❹

The fourth oil path 144, the second oil path 145, and the third oil path 146 are connected to each other at a connection portion (four) 143 °. The valve 143 is used to open and close the first oil path 144 and the third oil path 146, and the first oil Opening and closing between the path 144 and the second oil path 145. A motor 150 that drives the valve 143 is attached to the valve 143' as shown in FIG. The valve 143' is driven by the motor 15G to disconnect the third clutch II 70 from the fourth age unit 66. In summary, in the present embodiment, the actuator 1〇3 for applying the hydraulic pressure to the third clutch 70 and the fourth clutch 66 of the hydraulic clutch is constituted by the oil pump, the valve 143, and the motor 150. Then, the actuator 103 is controlled by the ecu 138 loyalty 4 &amp; U 138 shown in Fig. 18 to adjust the oil of the third clutch 70 and the fourth clutch 66. Specifically, (iv) the oil in the operation room 133 and the operation room 13 7 . Borrowing, preparing for the poor _ secret person stalks into the second clutch 70 and the fourth clutch 66 disconnected. More specifically, as shown in FIG. 18, the throttle opening sensor U2 and the vehicle speed sensor 88β are connected to the Ecu 138 as the foot 138 of the control unit according to the throttle opening sensor U2. The detected throttle opening degree and at least __ square of the vehicle speed detected by the vehicle speed sensing (4) are used to control the actuation of I34009.doc -59- 200928155 in the present embodiment as the ECU of the control unit. The 138 controls the actuator based on the throttle opening detected by the throttle opening sensor 112 and the squatting and squatting detected by the driver 8 8 103. Specifically, Lu's 138 is based on the v_N line diagram read from the memory 113, and is applied from the throttle opening degree outputted by the throttle opening degree sensor 112 and the vehicle speed outputted from the vehicle speed sensor 88. Information to control the actuator (9). Specifically, the valve 143 is formed in a substantially cylindrical shape. The valve 143 defines an internal path 149 for opening the inner path 148 of the path 144 and the second oil path 145 for opening the oil path 144 and the third oil path 146. The valve 143 is rotated by the motor 150 to select the first oil path 144 and the second oil path 145 to be opened by the internal paths (4), 149, and the first oil path 144 and the third oil path 146 are broken. The situation of the opening, the first oil path 144 is disconnected from the third oil path 146, and the first oil path 144 and the second oil path 145 are also disconnected, and the first oil path 144 and the third oil are Path 146 is open and any of the first oil path 144 and the second oil path 145 are also disconnected. Thereby, the state in which the fourth clutch "and the third clutch 70 are both off, the fourth clutch 66 is connected, and the third clutch 70 is off, or the fourth clutch 66 is off, and the third clutch is selected. Any of the states in which the clutch 70 is connected. - Operation of the shifting device 31 - Next, the operation of the shifting device 31 will be described in detail with reference to Fig. 9 to Fig. 12. When the engine is started, the first speed is reached. First, if the engine 30 is started, the crank is cranked. The shaft 34 (= input shaft 52) starts to rotate 134009.doc -60 - 200928155. The inner member 56 of the first clutch 55 rotates together with the input shaft μ. Therefore, the rotational speed of the input shaft 52 becomes a specific rotational speed (= If the first member 55 is turned on, the first shifting gear pair 86 will be turned on when the inner member 56 starts to apply a centrifugal force of a specific size or more. Rotating together with the outer member 57 of the first clutch 55. Thereby, the rotation of the input shaft 52 is transmitted to the first rotation axis. The fifth gear 87 rotates together with the first rotating shaft 53. Therefore, accompanied by

The first rotating gear pair 84 also rotates as the first rotating shaft 53 rotates. Therefore, the rotation of the first rotating shaft 53 is transmitted to the second rotating shaft 54 via the first transmission gear pair 84. The seventh gear 74 rotates together with the second rotating shaft 54. Therefore, with the rotation of the second rotating shaft 54, the second transmission gear also rotates. Therefore, the rotation of the second rotation tooth 54 by the second transmission tooth _5' is transmitted to the third rotation shaft 64. The thirteenth gear 79 is rotated in the same manner as the third rotating shaft 64. Therefore, with the rotation of the third rotating shaft 64, the third transmission gear pair 98 also rotates. Therefore, by the third transmission gear pair 98, the rotation of the third rotating shaft 64 is transmitted to the wheel. When the vehicle is moving forward, that is, when the speed is W, the first clutch 55 is transmitted. A shift gear pair 86, a -:=Γ, a second pass "wheel pair 85" and a third transfer gear pair transfer are transmitted from the input shaft 52 to the output shaft 33. ~2 speed ~ at the above 1 speed, and fifth The fourth gear 65 common to the gear 87 rotates together with the first rotating shaft 53. Therefore, the third gear 62 engaged with the fourth gear 65 and the inner member 60 of the second clutch 59 are also When the rotational density of the input shaft 52 rises, the rotational speed of the inner member 60 of the second clutch 59 also rises. If the rotational speed of the input shaft 52 becomes a second rotation faster than the first rotational reach Above the speed, the rotational speed of the inner member 60 also rises. 'The second clutch 59 is turned on as shown in Fig. 10. Here, in the present embodiment, the gear ratio of the second shift gear pair 83 is smaller than the first shift gear pair. Gear ratio of 86. Therefore, the rotational speed of the fourth gear 65

快 Faster than the rotational speed of the first gear 63. Therefore, the rotation is transmitted from the wheel-in shaft 52 to the first rotation shaft via the second transmission gear pair 83. On the other hand, the rotation of the first rotation shaft 53 is not transmitted to the input shaft 52 by the one-way rotation transmission mechanism %. The rotational force transmission from the first rotating shaft 53 to the output shaft 33 is performed via the first transmission gear pair 84, the second transmission gear pair 85, and the third transmission gear pair 98, as in the case of the first speed. When the vehicle is at the second speed, as shown in the figure, 'via the second clutch 59, the second shifting gear pair 83, the first transmission gear pair 84, the second transmission gear pair Μ and the third transmission gear pair 98, the rotation will be lost. The person (4) transmits to the output shaft 33 to the third speed. When the second speed is described above, if the rotational speed of the crank 34 (= input shaft 52) is higher than the first rotational speed 'and the vehicle speed becomes higher than the specific vehicle speed, then the figure is not as shown. The 'valve 143 is driven' third clutch 7 〇 is turned on. Therefore, the third variable gear pair 91 starts to rotate. Here, the gear ratio of the second transmission gear pair 91 is 134009.doc -62- 200928155 to the gear ratio of the second transmission gear pair 85. Therefore, the rotational speed of the tenth gear 77 of the third shift gear pair 91 is higher than the rotational speed of the eighth gear 78 of the second transmission gear pair 85. Therefore, the rotation of the second rotating shaft 54 is transmitted to the third rotating shaft 64 via the third shifting gear pair 91. On the other hand, the rotation of the third rotating shaft 64 is not transmitted to the second rotating shaft 54 by the one-way rotation transmitting mechanism 93. The rotation system of the third rotating shaft 64 is the same as that of the first speed and the second speed. The third shift gear pair 91 is transmitted to the output shaft 33.

Thus, as shown in FIG. 11, the second clutch 59, the first transmission gear pair 83, the first transmission gear pair 84, the third clutch 7〇, the first transmission gear pair 91, and the second transmission gear are shown in FIG. For 98, the rotation is transmitted from the input shaft 52 to the output shaft 33. ~4 speed ~ At the above 3 speeds, if the rotation speed of the crankshaft 34 (= input shaft 52) goes higher and the vehicle speed is higher, the valve (4) is driven as shown in Fig. 12. The fourth clutch (four) is connected. On the other hand, the third clutch (4) is broken. Therefore, the fourth shift gear pair 9 turns to start rotating. Here, the gear ratio of the fourth gear pair 90 is also smaller than the gear ratio of the second transmission # wheel pair 85. Therefore, the rotation speed of the twelfth gear 76 of the fourth transmission gear pair 90 is higher than that of the first transmission gear pair 85. The rotation of the rotational cam shaft 54 of the eight gears 78 is transmitted to the second rotating shaft 54 via the fourth shifting gear pair transmission mechanism 6 [on the other hand, the rotation J of the third rotating shaft 64 is transmitted to the second rotating shaft 54. The early rotation is transmitted to the output shaft 33 via the rotation system via the third rotation shaft 64 and the above-mentioned devout portion ～ 134009.doc -63 - 200928155. Thus, at the fourth speed, as shown in FIG. 12, via the second clutch 59, the first shifting gear pair 83, the first transmission gear pair 84, the fourth clutch 66, the fourth shifting gear pair 90, and the third transmission gear pair 98, the rotation is transmitted from the input shaft 52 to the output shaft 33. As described above, in the present embodiment, a so-called gear train type shifting device 31 is employed. Therefore, for example, the transmission loss of energy is less than that of the stepless transmission using the v-belt. As a result, the process of the vehicle can be improved.

e This embodiment is configured to shift between the input shaft 52 and the first rotating shaft 53, and between the second rotating shaft 54 and the third rotating shaft 64. Specifically, the first shift gear pair 86 and the second shift gear pair 83 are disposed between the input shaft 52 and the first turn axis 53. The second shifting gear pair 91 and the fourth shifting gear pair 9 are disposed between the second rotating shaft 54 and the third rotating shaft 64. Therefore, the structure 4 of the shifting device 31 can be simplified to miniaturize the shifting device 31 as compared with the case of using a shifting device such as a planetary gear that is disposed on a separate rotating shaft. In the present embodiment, the fourth gear 65 of the second shift gear pair 83 and the fifth tooth (10) of the first transmission gear pair 84 are common. Therefore, the variable speed display 31 can be further miniaturized. Further, in the present embodiment, the rotary shaft 53 and the third rotary shaft 64 are power transmission mechanisms for transmitting power between the shaft 52 and the output shaft 33. Further, in other cases, a chain guide or an input using a first so-called gear $^ wire provided for shifting is additionally provided. Therefore, it is not necessary to provide a chain or the like, and it is not necessary to provide a structure such as a chain fastener to suppress chain bounce, such as a 134009.doc-64-200928155 piece. Therefore, the structure of the shifting device 3 can be particularly simplified. In particular, the speed change device 31 can be miniaturized. In the present embodiment, the shifting device 31 is of the fourth speed. Therefore, compared with the speed change device of the speed, since the number of shifting stages is large with respect to the breadth of the speed region in which the vehicle is used, it is easy to realize comfortable automatic shifting. In the present embodiment, since the input shaft 52, the first rotating shaft, the second rotating shaft 54, the second rotating shaft 64, and the output shaft 33 are arranged in a direction perpendicular to the axial direction of the input vehicle w (ie, the front-rear direction), Therefore, with respect to the axial direction of the input shaft 52, the speed change device 31 can be miniaturized. As a result, the width of the lighter treadmill 2 in the vehicle width direction can be suppressed. Therefore, the light machine treadmill 2 can be largely taken. In particular, in the present embodiment, the upstream clutch group 81 and the downstream clutch group 82 are disposed at least partially overlapping each other with respect to the axial direction of the input shaft 52. Therefore, for example, compared with the upstream clutch group. 8] and the case where the downstream side clutch group 82 does not overlap with respect to the drawing direction of the input shaft 52' can further reduce the width of the shifting device 31 with respect to the axial direction of the input shaft 52. As a result, the light machine step can be further reduced. The width of the width direction of the vehicle 2 is considered. From the viewpoint of reducing the width of the vehicle width direction of the light motorcycle 2, the upstream clutch group 8 1 and the downstream clutch group 82 are preferably in the axial direction of the input shaft 52. Substantially heavy In the present embodiment, the first clutch 55 and the fourth clutch 66 are disposed such that at least a portion overlaps each other with respect to the vehicle width direction, and the second clutch 59 and the third clutch 70 are disposed in relation to the vehicle width direction. At least a portion overlaps each other. Therefore, the width of the shifting device 31 with respect to the axial direction of the input shaft 134009.doc - 65 - 200928155 52 can be further reduced. From the step-by-step reduction of the shifting device &amp; about the axial direction of the input shaft 52 In view of the width, the first clutch 55 and the fourth clutch 66 are preferably arranged to substantially overlap with respect to the vehicle width direction, and the second clutch 59 and the third clutch 7 are preferably configured to be related to the vehicle width direction. Further, in the present embodiment, in the axial direction of the input shaft 52, the first shift gear pair 86 and the fourth shift gear pair 9 are disposed at positions at least partially overlapping each other. The second shifting gear pair 83 and the third shifting gear pair are disposed at positions where at least the portions overlap each other. Therefore, the width of the speed reducing device 31 with respect to the axial direction of the input shaft 52 can be particularly widened. For example, it may be considered that the first shifting gear pair 86 is disposed on the right side of the first disengaged gear face, and the fourth shifting gear pair 9Q is disposed on the left side with respect to the second clutch gear 66. The second shifting gear (10) is disposed on the left side with respect to the second clutch H59, and the third shifting gear is disposed on the right side of the third clutching gear. In general, the first clutch 55 and the first clutch 55 listed in the front-rear direction may also be considered. a fourth clutch Μ, the second speed gear pair 86 and the fourth speed change gear (four) are disposed on opposite sides of each other

It is conceivable that the second shift gear (10) and the third shift gear (four) are disposed on the opposite side with respect to the second clutch T and the third clutch g 7〇' arranged in the front-rear direction. However, in the case of such a configuration, the width of the shifting direction becomes larger. The vehicle width of the vehicle 31: in its 'as in this embodiment', the fourth variable gear pair four clutch 66 is located on the same side of the first shifting gear pair 86_ on the side of the first person and the younger seat, and The third shift gear field 91 pairs ==: 134009.doc * 66 - 200928155 7 〇 is located on the same side of the second shift gear pair 83 on the side where the second clutch 59 is located, thereby suppressing the shifting device 31 The width of the car width direction. In the case of the first clutch 55 and the fourth clutch 66 arranged in the front-rear direction, the first shift gear pair 86 and the fourth shift gear pair 9〇 are disposed on the same side, and are arranged in the front-rear direction. The second clutch ” and the third clutch 70 are disposed on the same side of the second transmission gear pair 83 and the third transmission gear pair 91, and the width of the transmission 31 in the vehicle width direction can be suppressed.

From the viewpoint of suppressing the width of the shifting device 31 in the vehicle width direction, it is preferable to arrange the plurality of clutches arranged on the same rotating shaft adjacent to each other. Specifically, as in the present embodiment, the first clutch 55 and the second clutch 59 are disposed between the first shift gear pair 86 and the second shift gear pair 83. Preferably, the third clutch gear pair 91 and the fourth shift gear pair 9 are disposed between the third shift gear pair 91 and the fourth shift gear pair 9 。. For example, the third clutch 7A and the fourth clutch 66 can be formed by a centrifugal clutch. In this case, for example, when the third clutch 7 is disconnected when the fourth clutch μ is turned off when the rotational speed of the second rotary shaft 54 is low, the fourth clutch 66 cannot be connected and the third clutch 7 is disconnected. Open state. Therefore, in order to perform the power transmission between the second rotating vehicle "and the third rotating shaft 64" in the state in which both the third clutch 7''''''''''''''''' The one-way clutch or the one-way gear is therefore apt to complicate the structure of the shifting device 31. The third clutch 7〇 and the fourth clutch 66 are configured by the hydraulic clutch with respect to the same in the present embodiment. 'The third clutch 7〇 can be freely disconnected: 134009.doc -67- 200928155 The disconnector 66. Therefore, it is not necessary to additionally provide a one-way clutch or a one-way gear. Therefore, the structure of the shifting device 31 can be more simplified. <<Modification 1>> Person 0 Description H describes an example in which the outer member 55 of the first clutch 55 and the member 6 i of the second clutch 59 are constituted by the same member. However, the present invention is not limited to the structure. For example, as shown in FIG. 19, the first member 55 and the second clutch 59 member 61 may be separately provided. [Modification 2] In the above embodiment, the description is directed to the eighth gear 78. Configuring a one-way rotation transmission mechanism 93 However, the present invention is not limited to this configuration. For example, as shown in Fig. 20, the unidirectional rotation transmitting mechanism may be disposed on the seventh gear μ in the above-described embodiment, and the second gear Μ An example of the one-way rotation transmission mechanism 96 is disposed. However, the present invention is not limited to this configuration. For example, as shown in Fig. 21, the one-way rotation transmission mechanism 96 may be disposed on the first gear 58. [Modification 4] The description of the first clutch 55 and the second clutch 59 is between the first shift gear pair 86 and the second variable gear pair 83. However, the present invention is not limited thereto. For example, as shown in Fig. 22, A clutch is disposed on the left side of the first shifting gear pair 86 and the second clutch is disposed on the left side of the second shifting gear pair 83. Similarly, the third clutch 7 is described in the above embodiment. 134009.doc -68· 200928155 The fourth clutch 66 is disposed between the third shift gear pair 91 and the fourth shift gear pair %. However, the present invention is not limited thereto. For example, as shown in Fig. 22, the third clutch 70 is Third shifting gear The pair 91 is disposed on the left side, and the fourth clutch 66 may be disposed on the left side with respect to the fourth shift gear pair 9 。. Even in the case shown in Fig. 22, the input shaft 52, the first rotating sleeve 53, and the second rotating shaft 54. Since the third rotating shaft 64 and the output shaft 33 are arranged in the front-rear direction, the shifting device 31 having a narrow width can be realized. <<Other Modifications>> The above embodiment describes an example in which the engine 3 is a single-cylinder engine. In the present invention, the engine 30 is not limited to a single-cylinder engine. The engine 3〇 may be a multi-cylinder engine such as a two-cylinder engine. In the above embodiment, an example in which the output shaft 33 and the third rotating shaft 64 are separately provided is described. . However, the present invention is not limited to this structure. The output shaft 33 and the third rotating shaft 64 may be common. In other words, the rear wheel 18 may be attached to the third rotating shaft 64. In the embodiment, the first clutch 55 and the second clutch 59 are each constituted by a drum type centrifugal clutch. However, the present invention is not limited to this structure. The first clutch 55 and the second clutch 59 may be clutches other than the centrifugal clutch. For example, the first clutch 55 and the second clutch 59 are hydraulic clutches. In the above embodiment, the first clutch 55 and the second clutch 59 are respectively configured by a disc type hydraulic clutch. However, the present invention is not limited to this structure. The fourth clutch 66 and the third clutch 7A may also be clutches other than the hydraulic clutch. For example, the fourth clutch 66 and the third clutch 7 〇 134009.doc -69· 200928155 can be centrifuged away from a cry .α _ &quot; * device. However, the fourth clutch 66 and the third clutch 70 are preferably hydraulic clutches. Here, the first clutch 55, the second clutch 59, the fourth clutch "and the first yoke 70" are respectively a drum type or a disc type centrifugal clutch or a drum type or a disc type hydraulic clutch. - the clutch 55, the second clutch 59, the fourth clutch 66, and the third clutch 70 are all centrifugal clutches. The clutch 55, the second clutch 59, the fourth clutch 66, and the third clutch 70 are all hydraulic clutches. Further, the first clutch 55, the second clutch 59, the fourth clutch 66, and the third clutch 70 have a larger gear or a plurality of clutches that are centrifugal clutches, and the other gears are hydraulically biased. Specifically, only the first clutch 55 is a centrifugal clutch, and the other clutches 59, 66, 7〇 are hydraulic clutches. Conversely, the first clutch 55, the second clutch 59, and the The four clutches 66 and the third clutch 7 〇 are relatively large or one of the plurality of clutches are hydraulic clutches, and the smaller ones of the gears are centrifugal clutches. The type 丨, 2 and each modification will be described with respect to the case where the gear pair is directly engaged. However, the present invention is not limited thereto. The gear pair may also be indirectly engaged via a separately provided gear. As shown in FIG. 15, the first rotating shaft is configured such that the axis C2 of the first rotating shaft 53 is located higher than the axis of the third rotating shaft 64. However, the present invention is not limited to this structure. For example, the first rotating shaft 53 may be disposed such that the axis C2 of the first rotating shaft 53 is located lower than the axis C4 of the third rotating shaft. Specifically, the first rotation axis 134009.doc -70· 200928155 may be set such that the axis C2 of the first rotation axis 53 is located below the plane p. The third rotating shaft 64 is disposed such that the axis C4 of the third rotating shaft 64 is located above the plane p. In the above embodiment, a four-speed shifting device is exemplified to describe a suitable mode for carrying out the invention. However, the invention is not limited thereto. For example, the shifting device can be set to 3 or more. In this case, it is conceivable that the third rotating shaft 64 is provided with a further rotating shaft 2 shaft between the output shaft 33, and the further clutch and the further shifting gear pair are disposed on the two shafts. © "Definition of Terms and Conditions in This Manual" In this manual, "Motorcycle" is not limited to the so-called narrow-sized motorcycle. "Motorcycle" means the so-called generalized motorcycle. Specifically, in the present specification, "motorcycle" refers to all vehicles that are direction-shifted by tilting the vehicle, and "motorcycle"* is limited to the locomotive. At least one of the front wheel and the rear wheel may be constituted by a plurality of wheels. Specifically, at least one of the "motorcycle" wheel and the rear wheel may be a vehicle that is adjacent to each other. "Motorcycles" include at least motorcycles, pedal-type vehicles, light-duty treadmills and off-road vehicles. <<Variation 5>> In the above-described embodiment 1, an example in which three rotating shafts are arranged between the input shaft 52 and the output shaft 33 as shown in Fig. 2 will be described. Further, in the example shown in the above embodiment, as shown in FIG. 5, the axis C1 of the input 52, the axes C2 to C4 of the first to third rotation = axes 53, 54, 64 and the output shaft 33 are shown. The axis (4) is approximately arranged on the straight line on the side. However, the present invention is not limited to S; the arrangement of the rotation axis between the input shaft 52 and the output shaft 33 is also 134009.doc -71 - 200928155. Further, the axis of each of the rotating shafts disposed between the input shaft 52 and the output shaft 33 may not be located on a straight line passing through the axis C of the input shaft 52 and the axis C5 of the output shaft 33. Figure 23 is a cross-sectional view showing the engine unit of Modification 5. Fig. 24 is a schematic partial cross-sectional circle for explaining the arrangement of the rotating shaft of the engine unit of the fifth modification. Fig. 25 is a schematic view showing the configuration of an engine unit of Modification 5. As shown in Fig. 23 and Fig. 25, in the fifth modification, the fourth rotating shaft 24'' and the fifth rotating shaft 241 are disposed between the third rotating shaft and the output shaft (33). The fourteenth gear 80 is attached to the fourth rotating shaft 24〇 so as not to be rotatable. Further, the fourth rotating shaft 240 is rotatably attached to the fifteenth gear 315. The fifteenth gear 315 is engaged with the seventeenth gear 3 7 that is rotatably attached to the output shaft μ via the sixteenth gear 3 rotatably attached to the fifth rotating shaft 241. The fourth transfer wheel pair 32 is constituted by the fifteenth gear 315, the sixteenth gear 316, and the seventeenth gear 317. The rotation of the fourth rotating shaft 240 is transmitted to the output shaft 33 by the fourth transmission gear pair 32 。. As shown in Fig. 24, the axis C2 of the first rotating shaft 53 is located on the rear side from the axis ci of the input shaft 52. Further, the axis C2 of the first rotating shaft 53 is located on the lower side than the axis c 1 of the input shaft 52. The axis C2 of the first rotating shaft 53 is slightly lower than the plane P including the axis C1 of the input shaft 52 and the axis C5 of the output shaft 33. The axis C3 of the second rotating shaft 54 is located on the rear side from the axis C1 of the input shaft 52 and the axis C2 of the first red rotating shaft 53, respectively. The axis C3 of the second rotating shaft 54 is located above the axis C1 of the input shaft 52 and the axis C2 of the first rotating shaft 53, respectively. The axis C3 of the second rotating shaft 54 is located on the upper side than the plane p. 134009.doc •72· 200928155 The axis C4 of the third rotating shaft 64 is located on the rear side from the axis C1 of the input shaft 52, the axis C2 of the first rotating shaft 53, and the axis C3 of the second rotating shaft 54, respectively. The axis C4 of the third rotating shaft 64 is slightly above the axis C1 of the input shaft 52 and the axis C2 of the first rotating shaft 53. The axis C4 of the third rotating shaft 64 is located on the lower side than the axis C3 of the second rotating shaft 54. Third rotation. The axis C4 of the shaft 64 is located on the upper side than the plane P. The axis C7 of the fourth rotating shaft 240 is respectively smaller than the axis C1 of the input shaft 52, the axis C2 of the first rotating shaft 53, the axis C3 of the second rotating shaft 54, and the axis C4 of the third © rotating shaft 64. Located on the back side. The axis C7 of the fourth rotating shaft 240 is located above the axis C1 of the input shaft 52 and the axis C2 of the first rotating shaft 53, respectively. The axis C7 of the fourth rotating shaft 240 is located on the lower side than the axis C3 of the second rotating shaft 54. The axis C7 of the fourth rotating shaft 240 is substantially at the same height as the axis C4 of the third rotating shaft 64. The axis C7 of the fourth rotating shaft 240 is located on the upper side with respect to the plane P. The axis C6 of the fifth rotating shaft 241 is respectively smaller than the axis C1 of the input shaft 52, the axis C2 of the first rotating shaft 53, the axis C3 of the second rotating shaft 54, and the axis C4 of the third ® rotating shaft 64. The axis C7 of the fourth rotating shaft 240 is located on the rear side. The axis C6 of the fifth rotating shaft 241 is slightly above the axis C1 of the input shaft 52 and the axis C2 of the first rotating shaft 53, respectively. The axis of the fifth rotating shaft 241 ‘the center C6 is located lower than the axis C3 of the second rotating shaft 54, the axis C4 of the third rotating shaft 64, and the axis C7 of the fourth rotating shaft 240. The axis C 6 of the fifth rotating shaft 241 is located on the upper side than the plane P. Further, an oil reservoir 99 is formed below the input shaft 52, the first rotating shaft 53, the third rotating shaft 64, and the fourth rotating shaft 240. In the present embodiment, the reservoir 134 009009.doc • 73- 200928155 oil 0卩99 is formed on the front side than the core C7 of the fourth rotary pumping 240. The oil reservoir 99 is not formed below the axis C7 of the fourth rotating shaft 240 and the axis C6 of the fifth rotating shaft 241. The first and second rotating shafts 53, 54 are disposed at positions higher than the oil reservoir 99 when the locomotive 3 is in a stopped state. Further in the present embodiment, the gears 63, 65, 69, 73, 75, 74 provided on the first and second rotating shafts 53, 54 are also disposed above the position of the oil reservoir 99 when the locomotive 3 is in a stopped state. . (Industrial Applicability) D The present invention is useful for a segment type automatic transmission and a motorcycle. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a left side view of a scooter type vehicle of the first embodiment. 2 is a cross-sectional view of an engine unit of an embodiment 1. Figure 3 is a partial cross-sectional view showing the engine unit of the embodiment 1. Fig. 4 is a schematic view showing the structure of an engine unit of the embodiment 1. Fig. 5 is a schematic partial cross-sectional view showing the arrangement of the rotating shaft of the engine unit of the first embodiment. Fig. 6 is a partial cross-sectional view showing the engine unit of the configuration of the downstream side clutch group of the embodiment 1. Figure 7 is a conceptual diagram showing an oil circuit. Fig. 8 is a partial cross-sectional view showing an engine unit of an oil filter or the like. Fig. 9 is a schematic view for explaining a power transmission path at the time of the first speed of the shifting device. Fig. 10 is a schematic view for explaining a power transmission path at the time of the second speed of the shifting device. 134009.doc •74· 200928155 Fig. 11 is a schematic view for explaining the power transmission path at the third speed of the shifting device. Figure 12 is a view for explaining the mode of the power transmission path at the 4th speed of the transmission device. Fig. 8 is a left side view of the moped of the embodiment 2, and Fig. 14 is a light machine for the implementation type 2. The right side view of the treadmill. Figure 15 is a right side view of the engine unit of the embodiment 2.

Figure 16 is a cross-sectional view showing the engine unit of the embodiment 2. Figure 17 is a partial cross-sectional view showing the engine unit of the embodiment 2. Fig. 18 is a partial cross-sectional view showing the engine unit of the configuration of the downstream side clutch group of the embodiment 2. Fig. 19 is a schematic view showing the configuration of an engine unit of a modification. Fig. 20 is a schematic view showing the configuration of an engine unit of a second modification. Fig. 21 is a schematic view showing the configuration of an engine unit of Modification 3. Fig. 22 is a schematic view showing the configuration of an engine unit of Modification 4. Fig. 23 is a schematic view showing an engine unit of a fifth modification. Fig. 24 is a partial cross-sectional view showing the engine in a modification 5 in a simplified manner. Fig. 25 is a schematic view showing the structure of an engine unit of Modification 5 〇 [Description of main components] 1 scooter type vehicle (motorcycle) 2 light machine type treadmill (motorcycle) 20 engine unit 134009.doc -75· 200928155 30 Engine 31 shifting device 33 output shaft 52 input shaft 53 first rotating shaft 54 second rotating shaft 55 first clutch 56 inner member (input side clutch member) © 57 outer member (output side clutch member) 58 first gear 59 second Clutch 60 inner member (output side clutch member) 61 outer member (input side clutch member) 62 third gear 63 second gear 64 third rotary shaft 〇 65 fourth gear 66 fourth clutch • 67 inner member (input side clutch member) • 68 External member (output side clutch member) 69 No. - Gear 70 Third clutch 71 Internal member (input side clutch member) 72 External member (output side clutch member) 134009.doc -76- 200928155 ❹ ❹ 73 74 75 76 77 78 81 82 83 84 85 86 87 90 91 93 96 Ninth gear seventh gear sixth gear twelfth gear tenth Gear eighth gear upstream side clutch group downstream side clutch group second shift gear pair first transmission gear pair second transmission gear pair first shift gear pair fifth gear fourth shift tooth third shift tooth one-way rotation leaflet rotation transmission Wheelset wheel alignment mechanism 134009.doc •77-

Claims (1)

200928155 X. Patent application scope: A segmental automatic transmission device comprising a segment type automatic transmission device having more than 4 fans of an input shaft and an output shaft; and comprising: a first rotation shaft, a second rotation shaft and a a three rotating shafts each arranged in a direction perpendicular to an axial direction of the input shaft, wherein the third rotating shaft is coupled to the output shaft or constitutes the output shaft; the first clutch includes an input side clutch member, Its system and its former ◎ The input shaft rotates together; and the output side clutch member is rotatable relative to the input shaft; the pair of gears includes: 不 π ·,,, π % hoist-clutch output side clutch member Rotating together; and a second gear that meshes with the first gear and rotates with the first rotating shaft; the armor includes a member of the input crying σ 与 that rotates together with the input shaft and is replaceable with respect to the aforementioned input (4) The output side of the turn is separated from the two: and the first clutch is connected to the upstream clutch. The rotation speed of the input shaft is different from that of the second transmission gear pair. The output of the second clutch is called the disengagement member and the bite is combined with the "third record, and the third gear of the material and the front gear - the shift gear:: two - the fourth gear of the same rotation" and has a different interpretation Gear ratio; brother-transmission gear pair, its shafts 1 and 3: the fifth gear, which is rotated with the first rotation; and the sixth Ια^, the gear's and the fifth gear bite 134009.doc 200928155 First The second rotating shaft rotates together; the rotating shaft::: a pair of gears, comprising: a seventh gear 'which is screwed to the second and rotates; and a first gear that is tied to the seventh gear The third rotating shaft rotates together; and the C transmitting mechanism is disposed between the seventh rotating shaft and the seventh rotating gear, and transmits the rotation of the second rotating shaft to the second rotating: the seventh gear is not reversed The rotation is transmitted to the foregoing first: rotation: U or the second one-way rotation transmission mechanism, which is disposed in the rotation transmission; = front: between the eighth gears, the rotation of the shaft of the eighth gear is reversely reversed The third rotation point W is delivered to the eighth gear; the third clutch is included, and the input side is coupled to the second rotation shaft-same rotation member, and the front portion is rotated relative to the front second (four) (four); a second shifting gear pair, comprising a side clutch member-the same-rotating ninth gear clutch, and a third rotating shaft _ the same as the ninth gear and the first shifting gear And the Zth ten gear, and The gear ratio is different from that of the fourth gear, which includes the input side clutch member and the out-side clutch member that can rotate with respect to the 靛-axis, and rotates with the front L The shaft rotates the clutch group and is connected to the rotation speed of the downstream contracting shaft formed by the third contract, and the second rotation is different. 134009.doc 200928155 The fourth shifting gear pair includes the front side and the front side Clutch member __ four-clutch transmission β 4 and then the first eleventh 铨 η - the gear bite merges with the aforementioned first and the tenth round, with the twelfth tooth with _35 rotation Ploughing the gear ratio of each of the first shifting gear pair and the third idle gear pair; and the gear pair and the second; the second; the side clutch group and the downstream clutch group are arranged in relation to The axial direction of the input shaft is at least: configured as a segmented automatic transmission, wherein the positions where the knives overlap. =-the clutch system is located on one side and the side of the second clutch; the front fourth clutch is at least partially overlapped with the third clutch and the fourth clutch and the fourth clutch input shaft Position: phase: the first two clutches II and the third axis A3, the axis (four) is at the position where the input shaft is overlapped. ❹ 4. For example, the automatic transmission of paragraph 1 of claim 1, wherein the pair of four shifting gears are located on the side with respect to the fourth clutch: the same: the pair of gears relative to the first clutch And the shifting gear pair is located on the side opposite to the third clutch: the shifting gear pair has a segment type automatic shifting device with respect to the second clutch, wherein the first clutch is And the second clutch system is located between the first variable 134009.doc 200928155 speed 2 wheel pair and the second gear gear pair; the third clutch and the fourth clutch system are located in the third gear pair and Between the aforementioned fourth shifting gear pair. 5. The segmental automatic transmission of claim 3, wherein the first shifting gear pair and the front fourth shifting gear pair are disposed at least partially overlapping each other with respect to an axial direction of the input shaft. And the second shift gear pair and the third shift gear pair are disposed at positions where at least a portion overlaps each other. 6. The segmented automatic transmission of claim 1, wherein said second shifting gear has a smaller gear ratio than said first shifting gear pair; said first clutch is coupled to said input shaft at a rotational speed of When the rotation speed is higher than the second rotation speed, the rotation speed of the input shaft is lower than the first rotation speed; and the rotation speed of the second clutch is higher than the rotation speed of the input shaft. When the rotational speed is equal to or greater than the rotational speed, the rotational speed of the input shaft is not lower than the second rotational speed; and further includes: a third one-way rotational transmission mechanism disposed in the second gear and the foregoing a rotation between the rotating shafts transmits the rotation of the second gear to the first rotating shaft, and conversely does not transmit the rotation of the first rotating shaft to the second gear; or a fourth one-way rotation transmitting mechanism Between the input shaft and the first gear, transmitting the rotation of the input shaft to the first gear, and conversely not rotating the first gear Pass 134009.doc -4 · 200928155 handover to the input shaft; and the fourth gear and the fifth gear is common. 7. The segment type automatic transmission according to claim 1, wherein the third clutch and the fourth clutch are hydraulic clutches intermittently by oil pressure; and the third clutch and the fourth clutch When one of the parties is engaged, the other party is disconnected. A motorcycle comprising a segmented automatic shifting device as claimed in claim 1. 134009.doc